JP7177459B2 - Audio insulator, audio system, and design method for audio insulator - Google Patents

Description

The present invention relates to an audio insulator used in speakers, amplifiers, CD players, analog players, etc., for the purpose of improving sound quality.

In the field of audio, the pursuit of sound that is as close to the original sound as possible has been made in components such as amplifiers, speakers, CD players, and cables, which are audio equipment. Despite the transition from analog to digital and the introduction of various innovative technologies, there are still limits to the technology involved in the process from recording to playback. cannot be faithfully reproduced. One of the reasons why audio equipment cannot follow the original sound (for example, the sound of a live orchestra performance) is the influence of vibration on the audio equipment. As is well known, audio equipment generates vibration by itself and is affected by various vibrations from the outside. In the case of an amplifier, a "beat" is generated by the AC fundamental signal of the power transformer and its harmonic components. In the case of a CD player, the motor that rotates the disc is the source of vibration. In the case of a speaker, the reaction force of the voice coil that drives the cone vibrates the speaker enclosure (box) body. This vibration is transmitted to the floor where the speaker is installed, and excites the complex natural vibration modes of the entire room, including the floor. Disturbance vibrations superimposed intricately on the original sound vibrate the speaker itself again. It is hypothesized that the inter-modulation distortion that occurs at this time degrades the sound quality of the audio equipment, but the vibration caused by mutual interference between the audio equipment and the installation surface degrades the quality of the reproduced sound. It seems to be an unmistakable fact that it is an important factor that lowers.

One of the means for improving the sound quality of audio equipment is an insulator. In the analog era, insulators were installed mainly between the analog player and the floor to suppress howling, and were essential as a means of blocking the transmission of vibrations. With the shift from analog to CD players, insulators have come to be used not as a measure to prevent howling, but as a means of tuning to improve the sound quality of audio equipment and adjust the sound to the listener's taste. It is well known that the use of insulators changes the sound quality, but the mechanism that brings about this effect has not been fully elucidated theoretically, and has been developed empirically and through trial and error. many. There are two types of insulators that have been used in the past.

(1) Floating type insulator This type of insulator is intended to block vibration (shutout), and uses a shock absorber with low rigidity. As a buffer, there are those using rubber materials, those using spring coils, air floating boards that contain air, and those using the repulsive force of magnetic force.

(2) Hard Material Insulator Another type of insulator uses a hard material. In recent years, hard materials such as wood, resin, metal, ceramics, quartz, coral, etc., have been used to effectively absorb the vibrations generated by audio equipment and release them to the outside instead of the above-mentioned buffers. Things are invented and commercialized. In the case of a hard insulator, it is used as means for tuning reproduced sound using the character of a high-quality acoustic material. for example,
(i) metallic materials
Brass: Bright, brilliant sound
Copper: Solid and powerful Silver: Good core alignment, quick rise and fall of sound Gold: Plump and glossy
(ii) Wood-based materials
African ebony: hard but unexciting sound (used for musical instruments)
Striped ebony: Softer than African ebony Sakura: Soft and aromatic
The above (i) and (ii) are selected according to the listener's preference according to the characteristics of the audio equipment or the music genre to be reproduced.

An audio insulator having the features (1) and (2) of both the floating system and the hard material system described above is proposed by the present inventors and disclosed in Patent Document 1.
(1) Effect of completely blocking vibrations in the low-frequency audible range (2) Assisting effect of high-frequency vibrations exceeding that of conventional hard material insulators However, the above proposal is due to the vibration damping effect received from the member (spring coil) that is in close contact with the resonance member. , there is a problem that the acoustic characteristic improvement effect brought about by the resonance member is restricted.

In Patent Document 2, the structure of an audio insulator that solves this problem is disclosed by the proposal of the present inventors. 31(a) is a top view, FIG. 31(b) is a front sectional view, FIG. 32(a) is an AA sectional view of FIG. 31(b), and FIG. 32(b) is a BB sectional view of FIG. 31(b). is. 511 is an upper sleeve (resonant member), 512 is a lower sleeve, and 513 is a surge prevention member. The upper sleeve is configured for the purpose of adjusting the acoustic characteristics in the high frequency range of the audio equipment by utilizing the resonance phenomenon of the resonance member. A spring coil 514 is provided inside the upper sleeve 511 and the lower sleeve 512 . 515 is an intermediate spacer, and 516a, 516b, 516c are spherical members (point contact members). 517a, 517b and 517c are recesses formed on the upper surface of the intermediate spacer to accommodate the spherical members, and 518a, 518b and 518c are outer wall portions for preventing the spherical members from coming off during assembly. A tapered portion 519 formed on the inner bottom of the upper sleeve 511 is always in point contact with the spherical member. Reference numerals 520 and 521 are positioning portions for the spring coil 514, 522 is a fastening bolt for preventing separation of the upper sleeve 511 and the lower sleeve 512, 523 is the head of this fastening bolt, and 524 is a cylindrical portion formed on the lower sleeve 512. , 525 is a fastening portion of a fastening bolt 522, 526 is a through portion formed in the central portion of the intermediate spacer 515 through which the fastening bolt passes, and 527 is an open end of the upper sleeve. Reference numeral 528 denotes a device mounting portion for mounting an audio device 529, and 530 denotes an insulator installation surface (floor surface).

By providing the intermediate spacer 515 with the through portion 526 for the fastening bolt and fastening the upper sleeve 511 and the lower sleeve 512 together, the relative movement of the upper sleeve 511 and the lower sleeve 512 can be restricted. That is, the inside of the upper sleeve has a cavity for accommodating the spring coil, the anti-surging member, the intermediate spacer, and the spherical member, one end of which has a sealed structure, and the other end which is open to the atmosphere (free It has a cylindrical shape with an edge), that is, a shape similar to a "wind chime". The upper end of the upper sleeve 511 is not completely fixed, but is elastically supported by a spring coil 514 via the three spherical members and intermediate spacers 515 in the X-, Y-, and Z-axis directions.

That is, the insulator intervenes between the resonance member and the load support portion with a member that is in close contact with them by point contact or line contact. As a result, the vibration damping effect of the spring coil is reduced, and the acoustic characteristics in the high frequency range can be greatly improved. At the same time, the rigidity of the load-bearing portion can be increased, and the installation stability of the audio equipment can be improved.

Japanese Patent Application Laid-Open No. 2012-48808 Japanese Patent Application Laid-Open No. 2014-209398

The previously proposed insulator is composed of an upper sleeve 511 , a lower sleeve 512 and an intermediate member 515 . In order to prevent the spherical member 516 interposed between the resonance member 511 and the intermediate spacer 515 from coming off, the structure is configured as follows. That is, recesses 517a, 517b, and 517c formed on the upper surface of the intermediate spacer for accommodating the spherical members, and outer wall portions 518a, 518b, and 518c for preventing the separation of the spherical members, are all highly accurate. 3D part processing is required.

Further, the proposed insulator is configured as follows for "relative movement restriction" between the upper sleeve 511 and the lower sleeve 512. As shown in FIG. The intermediate spacer 515 is formed with a through portion 526 for the fastening bolt 522, and the lower sleeve 512 is configured in a cylindrical shape to accommodate the head 523 of the fastening bolt 522 that moves up and down. The upper end of the fastening bolt 522 is fixed to the resonance member, and the bolt head 523 is configured to hook onto the lower sleeve 512 . There was a request for measures to further improve the acoustic characteristics of the proposed insulator with a simple, low-cost configuration that does not require high-precision processing.

Specifically, the first invention includes an upper member on which an audio device is arranged, a load support portion configured by an elastic support member for supporting the load of the audio device, the load support portion and the upper portion. an intermediate member interposed between members or interposed between the upper member and the floor surface, and an intermediate member interposed between the upper member and the intermediate member and between the intermediate member and the upper member and hooking means for connecting so that the distance can be changed within a predetermined value.

That is, in the present invention, since the point contact member is provided between the upper member and the intermediate member, it is possible to reduce the vibration damping action received from the load support portion. At the same time, the point contact member is sandwiched between the upper member and the intermediate member, and the hooking means for connecting the two members is provided between the two members, thereby reducing the vibration damping effect as described above. It is possible to realize an insulator whose structure can be greatly simplified by integrating the upper member, the intermediate member, and the point contact member. Further, since the hooking means allows a change in the separation distance between the upper member and the intermediate member, the upper member or the intermediate member is arranged so as not to form a vibration transmission path from the floor surface to the audio equipment in a steady state. It is possible to prevent contact with any of the

More specifically, musical tones reproduced by audio equipment contain many overtone components, but according to the present invention, high-frequency overtones are accurately reproduced without being affected by vibration attenuation, thereby making the reproduced sound lively. to enhance musical expression. In addition, the improvement of the acoustic characteristics in the high frequency range improves the sense of localization, resolution, and sense of depth of the stereo sound image.

On the other hand, it is possible to avoid the occurrence of intermodulation distortion due to mutual interference with the floor surface due to the low-frequency vibration isolation characteristics determined by the rigidity of the load supporting portion and the mass of the audio equipment.

Specifically, in the second invention , the hooking means has one end fixed to either the intermediate member or the upper member and the other end hooked to either the upper member or the intermediate member. It is constructed.

That is, in the present invention, it is possible to realize a structure that prevents the point contact member from separating from each member while allowing the separation distance between the upper member and the intermediate member to change with a simple configuration.

Specifically, in a third aspect of the invention , the load support portion is arranged between the upper member and the floor surface, and the intermediate member is pressed toward the upper member by the load support portion. be.

That is, in the present invention, the point contact state by the point contact member can be maintained while the upper member and the lower member are placed on the load support portion.

Specifically, in the fourth invention , a plurality of the hooking means are provided between the upper member and the intermediate member, and the hooking means is separated from the axis of the upper member. and is provided substantially concentrically with respect to the axis.

That is, in the present invention, the upper unit can be handled independently of the lower unit by providing a plurality of hooking means between the intermediate member and the upper member.

Specifically, in the fifth aspect of the invention , a threaded portion for a connection member that connects the bottom surface of the audio equipment and the upper member is formed in the central portion of the upper member.

That is, in the present invention, by providing a plurality of hooking means for preventing the separation of the intermediate member and the upper member at a location away from the axis, the space in the central portion of the upper member can be utilized. A threaded portion is formed in this space for a connection member that connects the bottom surface of the audio equipment and the upper member.

Specifically, in the sixth aspect of the invention , the end surface of the intermediate member on the side of the load supporting portion is configured to be in close contact with the viscoelastic material.

That is, in the present invention, the influence of contact resonance of the upper member or the intermediate member that makes point contact with the point contact member can be avoided due to the damping action of the viscoelastic rubber that is placed in close contact with the intermediate member.

Specifically, in a seventh aspect of the invention , the load support portion is composed of viscoelastic rubber and a spring coil embedded in the viscoelastic rubber.

That is, in the present invention, by using a damping material composed of a spring coil embedded inside the viscoelastic rubber, contact resonance of the upper member or the intermediate member that makes point contact with the point contact member can be avoided. , can also serve as a load-bearing member for audio equipment.

Specifically, in an eighth invention , the viscoelastic material is formed in a substantially cylindrical shape,
The point contact member is arranged at a position radially adjacent to the upper end surface of the viscoelastic material on the upper member side end surface of the intermediate member.

That is, in the present invention, it is possible to reliably avoid the influence of contact resonance of the point contact member.

Specifically, in the ninth invention , the distance between the central portion of the point contact member and the outer surface of the viscoelastic material is r _x , and the distance between the outer peripheral end of the intermediate member formed in a disk shape and the viscoelastic material is The distance r ₀ of the outer surface is set to r _x <r ₀ /2.

That is, in the present invention, the positional relationship between the central portion of the point contact member and the outer surface of the load supporting portion made of a viscoelastic material is set to the above condition, that is, r _x <r ₀ /2. Therefore, the influence of contact resonance can be reliably avoided.

Specifically, the tenth invention is constructed under the condition that the average thickness h _b of the intermediate member is <3 mm.

That is, in the present invention, although the intermediate member has a thin plate shape, the resonance phenomenon of the intermediate member is suppressed, and the influence on the acoustic characteristics can be avoided. The reason for this is that the vibration damping action of the viscoelastic material in close contact with the intermediate member is utilized. Since this damping action can avoid resonance phenomena (including contact resonance), the thickness of the intermediate member can be a thin structure of h _b <3 mm. Therefore, it becomes possible to apply press working, and a significant cost reduction can be achieved.

Specifically, in the eleventh invention , the surface of the intermediate member, which is the surface facing the upper end surface of the viscoelastic material, has a stepped shape in the circumferential direction or radial direction, and the viscoelastic material and the surface of the intermediate member are partially in close contact with each other.

That is, in the present invention, when the load supporting member is composed of a plurality of members including a viscoelastic rubber and a spring, if the contact area between the intermediate member and the viscoelastic rubber is reduced, the insulator can be made of the viscoelastic rubber. It is noted that the reaction force received from is reduced. That is, according to the present invention, the influence of the viscoelastic rubber on the damping of the insulator as a whole can be adjusted.

Specifically, in the twelfth aspect of the invention , the threaded portion formed in the upper member is a female thread, and the bottom surface thereof is formed with a recess for accommodating the tip of a spike for audio equipment.

That is, in the present invention, before connecting the insulator of the present invention and the speaker with the connecting member, the sound quality improvement effect of the present insulator can be easily experienced for sound quality evaluation while the spike is attached to the speaker.

Specifically, in a thirteenth aspect of the invention , the load supporting portion is composed of a spring coil and a surge prevention member made of a viscoelastic material for avoiding the surge phenomenon of the spring coil, and the spring coil and the surge prevention member The upper end surface is in close contact with the surface of the intermediate member.

That is, in the present invention, the surging prevention member (viscoelastic rubber) used as means for avoiding the surge resonance phenomenon peculiar to the spring coil is brought into close contact with the lower end surface of the intermediate member. As a result, even when an elastic support member in which the spring coil and the viscoelastic rubber are separated is used, contact resonance in the point contact member can be avoided.

Specifically, in the fourteenth invention , the point contact member is a spherical member and makes point contact with the upper member and the intermediate member.

That is, in the present invention, the spherical member is arranged between the upper member and the intermediate member, so that the upper member can automatically align itself with respect to the intermediate member.

Specifically, a fifteenth aspect of the present invention is characterized by: an upper recess portion having a curved surface that accommodates a part of the spherical member formed on a surface of the upper member on the intermediate member side; a lower recessed portion having a curved surface that accommodates a part of the spherical member formed on the surface of the upper member; the spherical member is rotatably inserted between the upper recessed portion and the lower recessed portion; In a balanced state in which the audio equipment is mounted on the upper surface, the upper member and the intermediate member are configured to be horizontally movable relative to each other.

That is, in the present invention, the horizontal resonance frequency of the thrust ball section formed between the upper member and the intermediate member can be set independently of the vertical resonance frequency of the load support section. For example, by increasing the vertical rigidity of the load support portion, the horizontal resonance frequency alone can be sufficiently lowered while the installation stability of the insulator body is sufficiently enhanced.

Specifically, the sixteenth invention is characterized in that the audio device mounted on the upper member is a speaker having an excitation force in a horizontal direction.

That is, the present invention focuses on the vibration source of the speaker. In the case of a speaker, the horizontal reaction force of the voice coil that drives the cone vibrates the speaker enclosure itself. This vibration is transmitted to the floor where the speaker is installed, and excites the complex natural vibration modes of the entire room, including the floor. In this insulator, the horizontal resonance frequency f _SX0 of the thrust ball portion can be made sufficiently small. As a result, the horizontal vibration of the speaker that is propagated to the floor is greatly cut off by the anti-vibration action.

Also, for audio, the user applies one type of insulator with the same spring stiffness to the loudspeakers in a given mass range. In this case, if a conventional floating insulator is applied, the resonance frequency will be high if the speaker is lightweight. However, in the present invention, the horizontal resonance frequency _fSX0 of the thrust ball portion can be set low regardless of the mass of the speaker. That is, the anti-vibration action obtained regardless of mass can reduce the occurrence of intermodulation distortion due to mutual interference with the floor surface.

Specifically, in the seventeenth invention , the horizontal resonance frequency of a thrust ball portion composed of the point contact member, the upper member, and the lower member provided below the upper member is f _X0 , and the upper member is f X0 . The resonance frequency determined by the mass of the audio equipment mounted on the member and the horizontal rigidity of the single load support portion is _fH , and _fX0 < _fH .

That is, in the present invention, the horizontal resonance frequency of the insulator main body can be set lower than in the case of the single load support portion without depending on the mass of the mounted object.

Specifically, in the eighteenth invention , the curvature radius of the upper recessed portion is R _2B , the curvature radius of the lower recessed portion is R _2A , the radius of the spherical member is R ₁ , and the gravitational acceleration is g. the frequency

と定義し、前記上部部材に搭載されるオーディオ機器の質量をM、前記荷重支持部単体の水平方向ばね剛性をK _Hとして

, where M is the mass of the audio equipment mounted on the upper member, and K is the horizontal spring _stiffness of the load support unit alone.

とし、f_X0<f _Hとなるように構成したものである。

and _fX0 < _fH .

That is, in the present invention, the horizontal resonance frequency f _X0 determined from R _2A is the radius of curvature of the upper recessed portion, R _2B is the radius of curvature of the upper recessed portion, and R ₁ is the radius of the spherical member. can be set so that _fX0 < _fH as described above, where M is the horizontal direction spring stiffness of the load supporting portion alone, and _fH is the horizontal direction resonance frequency determined from _KH .

Specifically, the nineteenth invention is constructed so as to satisfy f _X0 <15 Hz.

That is, in the present invention, if the resonance frequency of the thrust ball portion is set to f _X0 <15 Hz, the insulator body must be able to avoid the influence of floor vibration even when the resonance frequency of the load support portion alone is f _H >15 Hz. The condition f _0SUM <15Hz can be maintained.

Specifically, the twentieth invention is constructed so as to satisfy f _X0 <8 Hz.

That is, in the present invention, if the resonance frequency of the thrust ball section is set to f _X0 <8 Hz, even if the resonance frequency of the load support section is set sufficiently high from the standpoint of installation stability,
An insulator having a low horizontal resonance frequency, which has been practically difficult in the past, can be realized.

Specifically, in the twenty-first invention , the intermediate member is composed of a plurality of plate-like members spaced apart from each other in the thickness direction, and the upper member and the uppermost plate-like member are separated from each other. A spherical member, which is the point contact member, is provided between each of the plate-shaped members, and a multistage thrust ball portion is formed.

That is, in the present invention, the horizontal resonance frequency can be set more finely by the thrust ball portion having a plurality of stages.

Specifically, in the twenty-second aspect of the invention , the thrust ball portion further includes a cylindrical fixing member having one end opened and fixed to the load support portion, and the upper member and the intermediate member are arranged in the fixing member. These side surfaces are housed so as to face the inner side surface of the fixed member, and sealing means for preventing dust from entering the spherical member constituting the thrust ball portion is provided between the side surface of the upper member and the It is characterized by being provided between the inner surface of the fixing member.

That is, in the present invention, it is possible to prevent, for a long period of time, the change in the horizontal resonance frequency due to the change in the point contact state due to the dust entering the portion where the spherical member is accommodated.

Specifically, in the twenty-third invention , the sealing means also serves as vibration damping means.

That is, in the present invention, it is possible to adjust the horizontal damping at the thrust ball portion.

Specifically, the twenty-fourth aspect of the present invention provides a shaft fixed to the upper member, penetrating the intermediate member in a non-contact manner and extending toward the load support section, and provided below the shaft and the load support section. an upper limit regulating portion that regulates the amount of upward movement of the upper member provided between the lower members, and a lower member that is provided below the shaft and the load support portion; and a lower limit regulating portion for regulating the amount of downward movement of the upper member.

That is, in the present invention, even when a large excitation force is generated due to an earthquake or the like, it is possible to limit the displacement range of the audio insulator and prevent large rocking vibration from occurring in the mounted audio equipment. Therefore, even a tall audio device can be prevented from overturning when an earthquake occurs.

Specifically, according to the twenty-fifth aspect of the present invention , an audio system comprising the above-described audio insulator and an audio device mounted on the audio insulator has a simple and low-cost configuration, and further enhances the sound. It can be an audio system with improved characteristics.

Specifically, in a twenty-sixth invention , an upper member on which an audio device is arranged on the upper surface side, a load support section made of an elastic member for supporting the load of the audio device, and a combination of the load support section and the upper member. an intermediate member interposed between or between the upper member and the floor surface, and an intermediate member interposed between the upper member and the intermediate member and brought into point contact with the upper member or the intermediate member and a hook for preventing the spherical member from detaching from between the intermediate member and the upper member by connecting the spherical member to the intermediate member and the upper member such that the distance between the intermediate member and the upper member can be changed within a predetermined value. means, an upper recess portion having a curved surface that accommodates a part of the spherical member formed on the surface of the upper member on the intermediate member side, and the spherical shape formed on the surface of the intermediate member on the upper member side A balanced state in which a lower recessed portion having a curved surface for accommodating a part of a member, and rotatably inserted between the upper recessed portion and the lower recessed portion, and the audio device mounted on the upper surface of the upper member. wherein the upper member and the intermediate member are relatively horizontally movable spherical members, wherein the mass of the audio equipment and the rigidity of the load bearing portion a vertical resonance frequency setting step of setting a vertical resonance frequency required by the audio device from and a horizontal resonance frequency setting step of setting the horizontal resonance frequency from the radius of the member.

That is, according to the present invention, it is possible to easily set an ideal resonance frequency for an audio insulator.

According to the present invention, an audio insulator having (1) vibration isolation effect in a low frequency range, (2) optimum damping (braking) characteristics in a high frequency range, and (1) and (2) above does not require complicated parts processing, And it can be realized with an extremely simple configuration. Due to the above (1), it is possible to avoid intermodulation distortion due to mutual interference with the installation surface. In addition, according to the above (2), by accurately reproducing many high-frequency overtone components contained in the musical sound reproduced by the audio equipment without being affected by vibration attenuation, the reproduced sound is given liveliness and musical expression is enhanced. be able to. In addition, the improvement of the acoustic characteristics in the high frequency range improves the sense of localization, resolution, and sense of depth of the stereo sound image. The effect is remarkable.

BRIEF DESCRIPTION OF THE DRAWINGS It is the insulator for audios which concerns on Embodiment 1 of this invention, Fig.1 (a) is a top view, FIG.1(b) is front sectional drawing in the AA cross section of Fig.1 (a). FIG. 2(a) is an exploded view as seen from the AA cross section of FIG. 1(a), and FIG. 2(b) is a view of each part locally united into a unit. Fig.3 (a) is a top view of an intermediate member, FIG.3(b) is BB sectional drawing of Fig.3 (a). FIG. 4(a) is a CC sectional view of FIG. 4(b), and FIG. 4(b) is a top view of the upper member. FIG. 2 is an enlarged view of the vicinity of the spherical member in FIG. 1; The figure which modeled the thrust ball part of this unit. Fig. 7(a) shows the case where the speaker is supported only by the elastic member, and Fig. 7(b) shows the case where the speaker is supported by the elastic member and the thrust ball portion. . 8(a) is a top view, FIG. 8(b) is a front cross-sectional view in the case of the minimum installed load, and FIG. 8(c) shows an audio insulator according to a second embodiment of the present invention. The front sectional view in the case of the maximum value. Fig.9 (a) is BB sectional drawing of FIG.9(b), FIG.9(b) is a bottom view. 10(a) is a top view, and FIG. 10(b) is a cross-sectional view along AA of FIG. 10(a). Fig.11 (a) is BB sectional drawing of FIG.11(b), FIG.11(b) is a bottom view. 12 shows an audio insulator according to Embodiment 4 of the present invention, FIG. 12(a) is a top view, and FIG. 12(b) is a cross-sectional view along line AA of FIG. 12(a). 13(a) is a top view of an audio insulator according to Embodiment 4 of the present invention, and FIG. 13(b) is a cross-sectional view along line AA of FIG. 13(a). 14 shows an audio insulator according to Embodiment 6 of the present invention, FIG. 14(a) is a front cross-sectional view, FIG. 14(b) is a top view of a connecting member, FIG. 14(c) is a front view, and FIG. (d) is a bottom view. Fig. 15(a) is a diagram showing a state in which the insulator is screwed to the speaker, and Fig. 15(b) is a diagram in which two insulators without two screws are additionally arranged under the bottom surface of the speaker. FIG. 11 is a front cross-sectional view of an audio insulator according to Embodiment 7 of the present invention; 17(a) is a front sectional view, and FIG. 17(b) is an AA sectional view of FIG. 17(a). FIG. 11 is a front cross-sectional view of an audio insulator according to Embodiment 9 of the present invention; 19(a) is a top view and FIG. 19(b) is a cross-sectional view AA of FIG. 19(a). FIG. FIG. 11 is a front cross-section of an audio insulator according to Embodiment 11 of the present invention; 21(a) is a top view, and FIG. 21(b) is a cross-sectional view along AA of FIG. 21(a). FIG. 22 shows an audio insulator according to a thirteenth embodiment of the present invention, where FIG. 22(a) is a top view and FIG. 22(b) is a cross-sectional view along line AA of FIG. 22(a). 24(a) is a view taken along line BB of FIG. 23(b), and FIG. 23(b) is a sectional view taken along line AA of FIG. 23(a). 24(a) is a top view, FIG. 24(b) is an AA cross-sectional view of FIG. 24(a), and FIG. 24(c) is FIG. 24(a). BB cross-sectional view. FIG. 25 is a front cross-sectional view showing an audio insulator according to a sixteenth embodiment of the present invention, which is a cross-sectional view taken along line AA of FIG. 24(a). FIG. 21 is a front cross-sectional view showing an audio insulator according to Embodiment 17 of the present invention; 27(a) is a top view and FIG. 27(b) is a cross-sectional view taken along line AA of FIG. 27(a). FIG. 28(a) is a top view, and FIG. 28(b) is a cross-sectional view taken along line AA of FIG. 28(a). Graph showing vibration isolation performance versus frequency for natural frequencies f ₀ =8 Hz and f ₀ =15 Hz. The figure which shows another form of the structure of a "holding". FIG. 31(a) is a top view and FIG. 31(b) is a cross-sectional front view of an already proposed audio insulator. 32(a) is a cross-sectional view along AA in FIG. 31(b), and FIG. 32(b) is a cross-sectional view along BB in FIG. 31(b).

[First Embodiment]
FIG. 1 shows an audio insulator according to Embodiment 1 of the present invention, showing a state in which a speaker is installed on the top. FIG. 1(a) is a top view, and FIG. 1(b) is a front cross-sectional view along the AA cross section (a cross-sectional view taken along a dashed line connecting points a, b, c, d, e, f, and g) in FIG. 1(a). is. Fig. 2(a) is an exploded view of each part seen from the AA section of Fig. 1(a), Fig. 2(b) is a view of each part locally united into a unit, Fig. 3(a) is a top view of the intermediate member 15, FIG. 3(b) is a BB sectional view of FIG. 3(a), FIG. 4 is the upper member 11, FIG. 4(a) is a CC sectional view of FIG. 4(b), FIG. 4(b) is a top view of the upper member 11. FIG. 11 is an upper member, 12 is a lower member, and 13 is a cylindrical load supporting member that supports the load of the audio equipment. This load bearing member comprises a viscoelastic rubber 14a and a spring coil (spring material) 14b embedded in the viscoelastic rubber by integral molding. An intermediate member 15 and a spherical member (point contact member) 16 are composed of three spheres (16a, 16b, 16c). 17a, 17b, and 17c are recesses formed on the upper surface of the intermediate member to accommodate the spherical members, and 18a, 18b, and 18c are recesses formed on the lower surface of the upper member to accommodate the spherical members. 19a, 19b, and 19c are retaining pins (retaining members), 20a, 20b, and 20c are through holes formed in the intermediate member 15 and pass through the retaining pins, and 21a, 21b, and 21c are formed on the lower surface of the upper member. is a prepared hole for fixing the retaining pin. The retaining pin can prevent the upper member 11 and the intermediate member 15 from coming off, and the state in which the spherical member is sandwiched between the upper member 11 and the intermediate member 15 can be maintained. A gap is set between the outer peripheral portion of the retaining pin and the inner peripheral surface of the through hole, and the head portion of the retaining pin and the bottom surface of the intermediate member so as to always maintain a non-contact state. ” is configured. The intermediate member is pressed toward the upper member by the load support portion, and the spherical member is pressed against the upper member by the intermediate member.

22 is a fixed sleeve fixed to the outer peripheral portion of the lower member 12, and 23 is a groove formed in a circular shape on the lower surface of the outer peripheral side of the upper member 11 so as to cover the upper tip portion 24 of the fixed sleeve. The depth of the groove 23 is set so that the upper tip 24 of the fixed sleeve is always hidden within the entire load range of the insulator.

Reference numeral 25 denotes a speaker mounted on the insulator (illustrated by imaginary lines), and 26 a connecting member for connecting the speaker and the upper member 11 of the insulator. Reference numeral 27a denotes a speaker-side threaded portion of the connecting member, and 27b denotes an insulator-side threaded portion of the connecting member. Reference numeral 27c denotes an intermediate portion of the connecting member, the outer surface of which is turret-processed. 28 is the upper end surface of the upper member 11 .

The lower member 12 and the intermediate member 15 are L-shaped in cross section on one side. The inner peripheral surface of the cylindrical load bearing member 13 is mounted so as to be vertically sandwiched between the lower member 12 and the intermediate member 15 . In the embodiment, three parts, the lower member 12, the intermediate member 15, and the load bearing member 13, are fixed with an adhesive. Further, the fixed sleeve 22 is fastened to the outer peripheral surface of the lower member 12 by a shrink fitting method. Reference numeral 29 denotes a threaded portion penetrating through the central portion of the upper member 11; 30, a fastening member press-fitted into the hollow portion at the center of the lower member; and 31, a threaded portion formed on the inner surface of the fastening member 30. . The load bearing member 13 integrated with the spring coil and the viscoelastic rubber is put into practical use in the industrial field as a vibration damping part (for example, product name: Spring Pad).

The main material of the viscoelastic rubber that constitutes this vibration damping part is a known vibration damping material composed of high damping elastomer (low rebound rubber, urethane rubber, foam rubber), etc. Embedded spring coil. When this vibration damping part is applied as an audio insulator, the vibration damping action in the low frequency range is sufficiently obtained, but due to the excessive vibration damping action of the viscoelastic rubber, the high frequency components that give life to the sound are attenuated. As a result, the outline of the sound becomes ambiguous, and there is a drawback that the sound quality becomes cloudy. FIG. 2(a) is an exploded view of each part seen from the AA cross section of FIG. 1(a), and FIG. 2(b) is a view of each part locally united into a unit. The "upper unit" composed of the upper member 11, the intermediate member 15, the spherical member 16, and the retaining pin 19 is called a thrust ball portion 32 (indicated by a dashed line). The upper member 11 and the intermediate member 15 of the thrust ball section, with rotation of the spherical member about a static point of equilibrium, are horizontally unobstructed and relative to each other on the order of at least 0.5 to 1.0 mm. It is movable. Also, the “lower unit” 33 is composed of the lower member 12 , the load bearing member 13 , the fixed sleeve 22 and the fastening member 30 . In the embodiment, the thrust ball portion 32 and the lower unit 33 were individually assembled and then integrated with an adhesive.

Now, the audio insulator of this embodiment also has the following features that the previously proposed insulator (Patent Document 2) does not have.

[1] Significant simplification of insulator structure As described above, the insulator of this embodiment is composed of two independent units, the "upper unit 32" and the "lower unit 33". The “upper unit” is composed of the upper member 11 , the intermediate member 15 , the spherical member 16 and the retainer pin 19 . The retaining pin 19 prevents the upper member and the intermediate member from coming off, and a gap is set so that the head of the retaining pin and the bottom surface of the intermediate member are kept in a non-contact state during normal operation. It has a structure of "hanging". Also, the “lower unit” 33 is composed of the lower member 12 , the load bearing member 13 , the fixed sleeve 22 and the fastening member 30 . The two units can be handled independently during assembly as previously described in FIG. Here, the above-mentioned "holding" is defined as a holding means that satisfies the following conditions.

(1) At steady state, member A (above-mentioned upper member) and member B (above-mentioned intermediate member) do not come into contact except through said spherical member (point contact member).
(2) In an emergency when a force separating the members A and B acts, the relative distance between the members A and B is kept constant to prevent the members A and B from separating.
Supplementing the above (1), in a steady state, the microvibration from the speaker propagates only through the route of "the upper member → the spherical member → the intermediate member", and the hooking means is this vibration propagation route. does not affect

In the present embodiment, the "holding" structure applies the retaining pin and fixes the retaining pin to the upper member side. In addition, a through hole is formed in the intermediate member 15 so as to maintain a non-contact state with the intermediate member at all times. Conversely to this configuration, as will be described later with reference to FIG. 30, the retaining member may be fixed to the intermediate member side so that the retaining member is normally kept in a non-contact state with respect to the upper member. good.

With the configuration of this embodiment, the insulator structure can be greatly simplified and the cost can be reduced. In this embodiment, the shape of the lower member 12 can be greatly simplified. In the case of the audio insulator disclosed in Patent Document 2, as shown in FIG. A fastening bolt 522 is provided. Between the head 523 of this fastening bolt 522 and the lower sleeve 512, a large pull-out force can occur in the dashed circle A in FIG. 29b. Therefore, the lower sleeve 512 needs to have a strong and thick structure. In this embodiment, the "upper unit 32" and the "lower unit 33" are configured independently, and the pulling force applied to the upper unit 32 does not affect the lower unit 33 side. Therefore, the lower member 12 constituting the lower unit 33 can be a thin plate pressed part or a resin molded part.

In this embodiment, the intermediate member 15 also has a thin structure that can be press-worked. Substantial cost reduction can be achieved by applying press work, which dramatically shortens the processing time, instead of cutting. For example, in the case of a lot of about 1,000 pieces, the cost difference is several thousand yen for cutting compared to several hundred yen for stamping. However, in the case of press working, the plate thickness of the processed part is restricted. The resonance characteristics of the insulator installed under the speaker have a great impact on the acoustic characteristics, regardless of whether it is a floating type or a rigid type. When the intermediate member is installed under the upper member via the spherical member, the resonance characteristics of the intermediate member affect the acoustic characteristics. Therefore, it is necessary to make the intermediate member thick so that it has a high resonance frequency (usually 10,000 Hz or higher) exceeding the audible range. However, in the case of the insulator of this embodiment, the resonance phenomenon of the thin plate intermediate member 15 was suppressed, and the influence on the acoustic characteristics could be avoided. The reason is that the vibration damping action of the viscoelastic material 214a in close contact with the intermediate member 15 is utilized. Since this damping action can avoid the resonance phenomenon (including the contact resonance described above), the average thickness of the intermediate member is a thin structure of h _b <3 mm, which allows press working.

In this embodiment, the sleeve covering the load bearing portion is fixed to the outer peripheral portion of the lower member 12 as a fixed sleeve 22 . The reason for this is that when the sleeve is provided on the upper member 11 side, the resonance characteristics determined by the shape and material of the sleeve greatly affect the acoustic characteristics. If a good acoustic material is used for the sleeve, the acoustic characteristics can be improved, as evidenced by the wind chime effect. However, since high-quality acoustic materials are expensive, in this embodiment for the purpose of structural simplification and cost reduction, an inexpensive material (resin, etc.) is used and a fixing sleeve that has no effect on acoustic characteristics is used. Structured. For this purpose, a circumferentially formed groove is formed on the lower surface of the outer peripheral side of the upper member 11 so as to cover the upper tip portion 24 of the fixed sleeve 22 . The depth of the groove 23 is configured so that the upper tip 24 of the fixed sleeve is always hidden within the range of the total load to be mounted on the insulator.

[2] Contact resonance of the thrust ball portion can be avoided.
The thrust ball portion used in this embodiment is formed by rotatably inserting a spherical member between the recess and the lower recess. Assume an extreme case in which the thrust ball portion is not supported by the vibration damping parts as in this embodiment but is directly installed on the rigid floor surface. In this case, it was found that a high-frequency (order of several hundred to several KHz) resonance phenomenon of unknown cause may occur. The frequency of occurrence depends on the weight of the speaker, the condition of the floor surface on which the insulator is installed, etc., but this phenomenon has not been observed in the past with conventional spring-type or air-type floating insulators. When this resonance phenomenon occurs, the quality of the reproduced sound in the high frequency range is remarkably degraded. As a result of careful investigation of the cause, it became clear that it was "contact resonance" of the point contact members supported by point contact with the upper and lower members.

Contact resonance is discussed as a problem when attaching a vibration sensor to an object to be measured, for example, in the field of measuring instruments. The resonance frequency determined by the spring stiffness (contact stiffness) of the contact surface between the sensor and the installation surface limits the measurement frequency range of the vibration sensor. When comparing (1) when the vibration sensor is manually fixed to the installation surface and (2) when it is screwed, the measurable frequency range of (2) is about 10 times greater than that of (1). , and In the case of an audio insulator supported by a spherical member, it has been found that this contact resonance has a considerable influence on the quality (sound quality) of reproduced sound. In view of this point, the insulator of the present embodiment is composed of parts with rough precision by press working, and supports the mounted load at a plurality of points (3×4=12 points). It has a configuration that can avoid contact resonance.

If the thrust ball section is supported by a highly rigid member, there is no guarantee that the load can be uniformly supported at multiple points (12 points), and areas with defective metal-to-metal contact (backlash, play) may occur, resulting in contact. Resonance. In this embodiment, the thrust ball portion is softly supported by the three-dimensionally deformable viscoelastic rubber, and contact resonance is avoided by the vibration damping action of the viscoelastic rubber.

FIG. 5 is an enlarged view of the vicinity of the spherical member 16a in FIG. Even if the contact stiffness between the spherical member 16a and the lower recessed portion 17a and between the spherical member 16a and the upper recessed portion 18a is small and contact resonance (upper and lower arrows 34) occurs, the intermediate member 15 is placed directly below the spherical member 16a. This resonance is quickly attenuated by the viscoelastic rubber 14a, which is a vibration-absorbing material placed in between. The closer the spherical member 16 is to the upper end face 35 of the viscoelastic rubber 14a, the more advantageous it is to suppress contact resonance. In FIG. 5, dashed line 36 indicates the case where the center of the spherical member is located away from the outer surface of load bearing member 13 . Let r _x be the distance between the center of the spherical member 36 and the outer surface of the load bearing member 13 , and r ₀ be the distance between the outer peripheral end 37 of the intermediate member 15 and the outer surface of the load bearing member 13 . In this case, it was found that by setting r _x <r ₀ /2, the above resonance phenomenon can be suppressed within a practically acceptable range. In order to avoid contact resonance, the lower recessed portion 17a for accommodating the lower end portion of the spherical member is formed directly on the intermediate member 15 without interposing another member, as shown in this embodiment. is preferred.

[3] Easy integration of the present insulator and audio equipment In this embodiment, the screw portion 29 formed at the center of the upper member 11 and the connecting member 26 are screwed together to facilitate integration of the audio equipment. can. For the screw portion for fastening the audio equipment side, for example, the spike fastening portion formed on the bottom surface of the speaker may be used. In this embodiment, the reason why the connecting member 26 can be screwed into the central portion of the upper member 11 is that the locking pin 19, which prevents the separation of the intermediate member and the upper member, is placed away from the shaft center. This is because a plurality of them are provided. That is, a threaded portion is formed in the central portion of the upper member 11 by utilizing the space of the axial center portion of the upper member. As long as the function required for the retaining pin is such that the relative position of the upper member 11 and the intermediate member 15 can be maintained within a range that prevents the spherical member 16 from being detached, any structure may be used. For example, a stepped screw structure in which the depth of the screw hole for fastening with the upper member 11 is restricted (not shown). Although the retainer pin 19 is fixed to the upper member side in this embodiment, it may be fixed to the intermediate member side. In this case, a through hole may be formed in the upper member to accommodate the head portion of the retaining pin and the small-diameter portion in a non-contact manner (not shown).
The threaded portion 31 provided on the bottom surface of the lower member may be used, for example, as a means for installing and fixing a small speaker to a speaker stand. In this case, a through hole may be formed in the mounting surface of the speaker stand, and the insulator may be fixed with a bolt from the bottom surface of the speaker stand using the through hole.

[4] Horizontal vibration isolation and vibration isolation performance can be greatly improved As described above, the thrust ball portion in the present embodiment has a curved surface that accommodates a part of the spherical member formed on the upper member. a lower recess having a curved surface for accommodating a portion of the spherical member formed in the lower member; and the spherical member being rotatable between the upper recess and the lower recess. The upper member and the intermediate member are configured to be horizontally movable relative to each other in an equilibrium state in which the device is inserted and the device is mounted on the upper surface of the upper member. By interposing this thrust ball portion between the on-board equipment and the elastic support member that supports the load of the on-board equipment, various effects that could not be obtained with conventional insulators (or vibration isolation devices or vibration isolation devices) can be achieved. Obtainable. First, the analysis for obtaining the horizontal resonance frequency of the thrust ball portion will be described.

(1) Analysis for obtaining horizontal resonance frequency Fig. 6 shows a simplified model of the unit with one spherical member and one elastic support member. R ₁ is the radius of the sphere centered at O ₁ of the spherical member 16a, R _2A is the radius of curvature of an imaginary circle centered at O _2A of the lower recess 17a, and R _2B is the radius of curvature centered at O _2B of the upper recess 18a. is the radius of curvature of the virtual circle A payload weight Mg is constantly applied to the upper member. In the figure, a horizontal external force acts on the upper member, the spherical member rotates while contacting the inner surfaces of the upper and lower recesses 17a and 18a, and the upper member 11 is horizontally displaced with respect to the intermediate member 15. A state (relative displacement x ₁ ) is assumed.

Let T be the vertical drag force generated at the contact point A between the spherical member 16a and the upper recessed portion 18a. The vertical force component T _Y of T is balanced with the weight Mg of the payload, and the horizontal force component T _X (=Mg·tan θ) of T becomes the restoring force. Therefore, the horizontal stiffness is K _SX =T _{X /} x1.

The horizontal stiffness at equilibrium θ=0 is

The horizontal motion equation at this time is

Therefore, the resonant frequency f _SX0 is

From equation (5), the resonance frequency f _SX0 does not depend on the mass M of the mounted object, and can be determined only by the radius R ₁ of the spherical member 16a, the curvature radius R _2B of the upper recess 18a, and the curvature radius R _2A of the lower recess 17a. I know it will be decided. A case where R ₂ =R _2A =R _2B will be described below. Assuming that the displacement of the thrust ball portion is x ₁ and the displacement of the load bearing portion is x ₂ , the displacement of the upper member 11 with respect to the floor is x=x ₁ +x ₂ .
(i) When R ₂ =R ₁ , since the upper member and the intermediate member do not move relative to each other, the horizontal stiffness and resonance frequency of the thrust ball portion are K _{SX0 ≈∞} and f _SX0 →∞.
(ii) When R ₂ >>R ₁ , the horizontal stiffness and resonance frequency of the thrust ball portion are reduced to K _SX0 →0 and f _SX0 →0 from equations (3) and (5).
(iii) Since the vertical rigidity of the thrust ball portion is sufficiently higher than the horizontal rigidity, the horizontal rigidity of the present insulator can be set sufficiently small regardless of the rigidity of the load supporting portion.

In the case of the prior art without the thrust ball portion, the resonance frequency can be reduced even if the rigidity of the load support portion (the spring coil and the viscoelastic rubber) is reduced. However, from the conditions of (1) the required vibration isolation characteristics for the floor, (2) the installation stability of the load, and the above conditions (1) and (2), the vertical and horizontal resonance frequencies are usually f ₀ =8 to 15Hz. is constrained to the range of In this embodiment, since the vertical rigidity of the thrust ball portion is sufficiently high, only the horizontal rigidity can be set small while maintaining the vertical resonance frequency within the above range. Table 1 shows the calculation results of the horizontal resonance frequency f _SX0 when the radius R ₁ of the spherical member and the curvature radius R ₂ of the upper and lower recesses are changed by four types.

As shown in Table 1, both the spherical member radius R ₁ and the curvature radius R ₂ of the upper and lower recessed portions 3 are within practically feasible ranges, and the horizontal resonance frequency f _SX0 of the thrust ball portion can be reduced. . For the above reason, the present insulator has the following effects.

(2) "Micro-vibration/seismic isolation slider effect" --- Reduces the effect of vibrating the floor It also affects other audio equipment. Note that the direction of vibration generated by many audio devices is horizontal. In the case of a speaker, the horizontal reaction force of the voice coil that drives the cone vibrates the speaker enclosure itself. This vibration is transmitted to the floor where the speaker is installed, and excites the complex natural vibration modes of the entire room, including the floor. In this insulator, the horizontal resonance frequency f _SX0 of the thrust ball portion can be made sufficiently small. As a result, the horizontal vibration of the speaker that is propagated to the floor is greatly cut off by the anti-vibration action. Furthermore, horizontal vibration of the floor surface is not fed back to the speaker side due to the vibration isolating action of this insulator. By the way, the action of isolating the vibration of the mounted object so that it is not transmitted to the floor side is called "vibration isolation", and conversely, the action of isolating the vibration from the floor so that it is not transmitted to the mounted object is called "vibration isolation". Vibration”. Figures 7(a) and 7(b) are conceptual diagrams of the "micro-vibration/seismic isolation slider effect" found in this research.

FIG. 7(a) shows a model of a case where the load supporting member is only an elastic supporting member (including the spring coil and the vibration damping part 13 of the embodiment). 851 is a speaker which is an on-board device, 852 is a voice coil as a horizontal drive source, 853 is a floor surface, and 854a and 854b are front side and rear side elastic support members. In FIG. 7(a), when a horizontal reaction force F _X is applied to the voice coil 852, the speaker tilts as indicated by an imaginary line (double-dot chain line). Since an AC signal is input to the voice coil 852, the speaker 851 undergoes rocking vibration that sways from side to side. As a result, the vertical reaction forces T _z1 and T _z2 from the elastic support members act on the floor surface 853 with the positive and negative reversed. As mentioned above, this vibration is transmitted to the floor on which the speaker is installed, and excites the complex natural vibration modes of the entire room, including the floor. Disturbance vibrations superimposed intricately on the original sound vibrate the speaker itself again. The intermodulation distortion that occurs at this time degrades the sound quality of audio equipment.

FIG. 7(b) shows a modeled case where the thrust ball portion is attached to the elastic support member. 855a and 855b are upper members, 856a and 856b are spherical members, and 857a and 857b are lower members. If the horizontal stiffness of the thrust ball portion is sufficiently small, the horizontal reaction force F _X acting on the voice coil 852 will balance the horizontal inertial force of the speaker body. As a result, the vertical reaction forces T _z1 and T _z2 due to the rocking vibration that swings from side to side are greatly reduced.
By reducing the vertical reaction forces T _z1 and T _z2 , the vibration that excites the floor surface is also reduced, so the occurrence of intermodulation distortion can be suppressed. This effect is obtained when the horizontal stiffness is sufficiently smaller than the vertical stiffness of the elastic support member in the range of micro-vibration, and is called "micro-vibration/seismic isolation slider effect". by the way,
(i) The stiffness in the vertical and horizontal directions of a general elastic support member cannot be designed independently. If the horizontal stiffness is lowered, the vertical stiffness is also lowered.
(ii) The horizontal rigidity of the thrust ball portion (spherical member + hollow portion) can be arbitrarily set by setting the parameters (R ₁ , R _2A , R _2B ). However, the vertical stiffness K _{SH0 ≈∞} .

Therefore, the combination of (i) + (ii) allows the rigidity of the elastic support member to be adjusted to the following: A system with low stiffness and low resonance frequency only in the horizontal direction can be realized while maintaining the conditions. Moreover, the horizontal resonance frequency is not affected by the mounted mass.

(4) Effect when applied to speakers The vibration isolation characteristics of the thrust ball section, which allows the horizontal direction to have a low resonance frequency and the resonance frequency is not affected by the mounting mass, is practical when applied to small speakers. Extremely effective. The reason for this will be explained below.

When applying the floating insulator as in the present embodiment to an audio speaker, a variety of insulators are available according to the mass range of the speaker. The reason is that, for the same spring stiffness K, the resonance frequency f ₀ [see formula (11)] changes depending on the mass m of the speaker. As described above, (1) the required vibration isolation characteristics for the floor surface, (2) the installation stability of the mounted object, and the above conditions (1) and (2), the vertical and horizontal resonance frequencies are usually f ₀ = It is preferable to set it in the range of 8-15Hz. In the audio field, the mass of speakers that are commonly used is m=20-80Kg for large size and m=3-20Kg for small size. Here, it is assumed that among conventional insulators having no thrust ball portion, insulators having two types of spring stiffness for small size and large size are available. Table 2 shows the case where the mass of a small speaker is m=20 Kg and the resonance frequency is set to f ₀ =8 Hz.

From Table 2, it can be seen that the mass m=3 Kg and the resonance frequency f ₀ =20.7 Hz, which greatly deviates from the condition f ₀ <15 Hz required for the resonance frequency. However, in the case of the insulator of the present invention in which the thrust ball portion and the elastic support member are combined, the above-mentioned "micro-vibration/seismic isolation slider effect" reduces the vibration excited on the floor surface by the speaker as the drive source. As a result, increasing the vertical resonance frequency in a small speaker can suppress the occurrence of intermodulation distortion.

(5) Optimum damping (braking) characteristics in the high frequency range can be obtained. In this embodiment, the spherical member 16 is in close contact with the intermediate member 15 fixed to the upper end surface of the vibration absorbing member and the upper member through point contact. Therefore, the influence of the vertical vibration damping action from the viscoelastic rubber side acting on the upper member can be reduced. Furthermore, the horizontal vibration isolation characteristics between the upper member and the viscoelastic rubber side are added to the effect of the point contact, thereby further suppressing the attenuation of high frequency components received from the viscoelastic rubber. . To enhance musical expression by giving liveliness to reproduced sound by accurately reproducing high-frequency harmonics without the influence of vibration damping, since musical sounds reproduced by audio equipment contain many overtone components. can be done. Further, the improvement of the acoustic characteristics in the high frequency range can improve the sense of localization, resolution, and sense of depth of the stereo sound image.

[Second embodiment]
FIG. 8 shows an audio insulator according to Embodiment 2 of the present invention, in which the influence of the viscoelastic rubber on the overall damping of the insulator is adjusted by reducing the contact area between the viscoelastic rubber upper end surface and the intermediate member. It is what I did. Fig. 8(a) is a top view, Fig. 8(b) is a cross-sectional front view when the load on the insulator is the minimum value, Fig. 8(c) is a cross-sectional front view when the load on the insulator is the maximum value, Fig. 9 indicates an intermediate member, FIG. 9(a) is a cross-sectional view along BB in FIG. 9(b), and FIG. 9(b) is a bottom view.

8(a) and 8(b), 211 is an upper member, 212 is a lower member, and 213 is a load bearing member. This load bearing member is composed of a viscoelastic rubber 214a and a spring coil (spring material) 214b. An intermediate member 215 and a spherical member (point contact member) 216 are composed of three spheres (216a, 216b, 216c). 217a, 217b and 217c are lower depressions formed on the upper surface of the intermediate member to accommodate the spherical members, and 218a, 218b and 218c are upper depressions to accommodate the spherical members formed on the lower surface of the upper member. be. 219a, 219b, and 219c are retaining pins; 220a, 220b, and 220c are through holes formed in the intermediate member 215 and pass through the retaining pins; This is the pilot hole for the pin. 222 is a fixed sleeve, 223 is a groove, 224 is an upper tip of the fixed sleeve, 225 is a speaker (illustrated by an imaginary line), 226 is a connecting member, and 227a and 227b are the speaker side, the insulator side, and the middle of the connecting member, respectively. 227c is an intermediate portion; 228 is the upper end surface of the upper member 211; 229 is a threaded portion formed at the center of the upper member, 230 is a fastening member, and 231 is a threaded portion formed on the inner surface of this fastening member.

9(a) and 9(b), 232a is a protrusion on the bottom surface of the intermediate member 215, 232b is a recess on the bottom surface of the intermediate member 215, and 233 is the upper end surface of the viscoelastic rubber. Protrusions 232a and recesses 232b are alternately formed on the bottom surface of the intermediate member 215 in the circumferential direction, and the protrusions 232a are in close contact with the upper end surface 233 of the viscoelastic rubber. The angle at which the projection 232a is formed is θ ₂ , and the angle at which the projection 232a and the recess 232b are formed is θ ₁ +θ ₂ . At this time, the angle at which the bottom surface of the intermediate member 215 contacts the upper end surface of the viscoelastic rubber is reduced to θ ₂ /(θ ₁ +θ ₂ ) in this embodiment.

As described above, in this embodiment, the load supporting member is composed of two members, the viscoelastic rubber 214a and the spring coil 214b. Therefore, the magnitude of the reaction force that the intermediate member receives from the viscoelastic rubber can be reduced by reducing the contact area between the intermediate member and the viscoelastic rubber. The reason will be explained by a simple theoretical analysis. Assuming that the spring stiffness of the spring coil is K _S , the spring stiffness of the viscoelastic rubber is K _D , and the load applied to the insulator is F, the displacement X ₁ when the intermediate member and the viscoelastic rubber are in full contact is

When the contact area between the intermediate member and the viscoelastic rubber is n times, the spring stiffness of the viscoelastic rubber is K _D →n K _D . Then the displacement X ₂ is

The magnitude of the reaction force that the intermediate member receives from the viscoelastic rubber is proportional to displacement×contact area. If F _D1 is the magnitude of attenuation when the entire surface is in close contact,

The magnitude of the reaction force F _D2 at the time of partial contact is

The ratio of the magnitude of the reaction force between partial contact and full contact is

When the contact area is reduced, n<1, so F _D2 <F _D1 . In summary, if the contact area between the intermediate member and the viscoelastic rubber is reduced, the reaction force that the insulator receives from the viscoelastic rubber is reduced. That is, for the same external force F, the ratio of the reaction force received from the viscoelastic rubber (the ratio of the load bearing on the viscoelastic rubber) is (F _D2 /F)<(F _D1 /F). The smaller the contact area of the viscoelastic rubber, the smaller it becomes. For example, if we assume that K _S =5, K _D =5, and n=1/3, we know that F _D2 /F _D1 =1/2.
However, if the load-bearing member is composed of only a single member of viscoelastic rubber, since K _S =0, F _D2 =F _D1 from equation (10), and the magnitude of the reaction force depends on the contact area. Independent.
The magnitude of the reaction force from the viscoelastic rubber also corresponds to the magnitude of damping in the dynamic vibration state, and according to this embodiment, the influence of the viscoelastic rubber on the damping of the insulator as a whole can be adjusted.

[Third embodiment]
FIG. 10 shows an audio insulator according to Embodiment 3 of the present invention. Similar to the embodiment described above, by reducing the contact area between the upper end surface of the viscoelastic rubber and the intermediate member, the viscoelastic rubber becomes is adjusted for the effect on the attenuation of 10(a) is a top view, FIG. 10(b) is a front sectional view, FIG. 11 shows an intermediate member, FIG. 11(a) is a BB sectional view of FIG. 11(b), and FIG. 11(b) is a bottom view. It is a diagram.

10(a) and 10(b), 250 is an intermediate member, 251 is a bottom surface of this intermediate member, and 252 is a ring formed on the bottom surface 251 and having a convex cross section. The ring bottom surface is in close contact with the upper end surface 233 of the viscoelastic rubber over the entire circumference. In _FIG . 11(a), if the width of the upper end surface 233 of the viscoelastic rubber is d1, and the width of the ring in close contact with the _upper end surface 233 is d2, the bottom surface 251 of the intermediate member is the width of the viscoelastic rubber. _The area in close contact with the upper end surface 233 is reduced to d2 _/ d1 in this embodiment. According to this embodiment, the influence of the viscoelastic rubber on the damping of the insulator as a whole can be adjusted in the same manner as in the above-described embodiments. This may be combined with the method of adjusting the attenuation by setting the angles at which the projections 232a and the recesses 232b are formed in the above-described embodiment.

[Fourth Embodiment]
FIG. 12 shows an audio insulator according to Embodiment 4 of the present invention, in which a thrust ball structure with infinite horizontal rigidity is applied. FIG. 12(a) is a top view, and FIG. 12(b) is a front cross-sectional view along the AA cross section (cross-sectional view taken along a dashed line connecting points a, b, c, d, e, f, and g) of FIG. 12(a). is. 551 is an upper member, 552 is a lower member, 553 is a load bearing member, 554 is an intermediate member, and 555 is a spherical member, which consists of three spheres (555a, 555b, 555c). Numerals 556a, 556b, and 556c are recesses formed on the upper surface of the intermediate member to accommodate the respective spherical members, and 557 is a spherical member storage portion formed on the lower surface of the upper member, which accommodates the three spherical members and points. A contacting tapered portion 558 is formed.
559a, 559b and 559c are retaining pins, 560a, 560b and 560c are retaining pin through holes, 561 is a fixing sleeve, and 562 is audio equipment. Focusing on the spherical member 555a, a normal force T acts on the upper portion of the spherical member 555a at the point of contact with the tapered portion 558 due to the load of the mounted object. A reaction force corresponding to the radial component force T _x of this normal force T acts as a force directed toward the center of the spherical member 555a. The lower portion of the spherical member 555a is housed in a recessed portion 556a and its movement in the radial direction is restricted. Also, the intermediate member 554 in which the recessed portion is formed is in close contact with the load supporting portion 553 . That is, the intermediate member is pressed toward the upper member by the load support portion, and the point contact member is pressed against the upper member by the intermediate member. With the above configuration, the upper member and the intermediate member of the _insulator of the present embodiment do not move relative to each other when the audio equipment is mounted. _SX0 → ∞. Since the vibration path from the audio equipment to the elastic support member includes a point-contact transmission path, the vibration damping action in the high frequency range can be suppressed. Further, as in the first embodiment, (1) the lower member 552 can be a thin plate pressed part or a resin molded part. (2) Effects such as avoidance of contact resonance of the thrust ball portion can be similarly obtained.

[Fifth Embodiment] Spikes Instead of Balls In the above-described embodiments, the members interposed between the upper member and the intermediate member were all spherical members. In this embodiment, instead of the spherical member, the contact portion is configured by a spike having a one-point contact. FIG. 13(a) is a top view of an audio insulator according to Embodiment 4 of the present invention, and FIG. 13(b) is a sectional view along AA. 13(a) and 13(b), 300 is an upper member, 301 is a lower member, 302 is a load bearing member, and this load bearing member 302 is composed of a viscoelastic rubber 302a and a spring coil (spring material) 302b. . An intermediate member 303 and a bolt 304a are composed of a screw portion 305a and a spike portion 306a. 308a is a recess for accommodating the tip of the spike formed on the lower surface of the upper member. The bolts and the recessed portions are arranged in the circumferential direction, and are equally divided into three sets. 309a, 309b, 309c are retaining pins; 310a, 310b, 310c are through holes formed in the intermediate member and pass through the retaining pins; It is a pilot hole for the pin (310b, 311b not shown). 312 is the upper end surface of the viscoelastic rubber, 313 is a fixing sleeve, 314 is a speaker (illustrated by imaginary lines), and 314 is a connecting member.

In the present embodiment, the spike portion 306a is provided on the intermediate member 303 side and the recessed portion 308a is provided on the upper member 300 side, but the arrangement may be reversed. Moreover, instead of attaching the spike portion as a separate part, the protrusion is formed on the intermediate member by utilizing the fact that the intermediate member can be a thin pressed part. A configuration in which the tip of this protrusion is used as a spike tip may be used. (not shown)

In this embodiment, as in the previous embodiment, since the upper member and the intermediate member do not move relatively, the horizontal stiffness and resonance frequency of the thrust ball portion are K _{SX0 ≈∞} and f _SX0 →∞. Since the vibration path from the audio equipment to the elastic support member includes a point-contact transmission path, the vibration damping action in the high frequency range can be suppressed. Further, as in the first embodiment, (1) the lower member 552 can be a thin plate pressed part or a resin molded part. (2) Effects such as avoidance of contact resonance of the thrust ball portion can be similarly obtained.

[Sixth embodiment]
FIG. 14 shows an audio insulator according to a sixth embodiment of the present invention, and shows a case where a connecting member having two upper and lower screw outer diameters different in diameter is used to connect the audio equipment and the insulator. 14(a) is a front sectional view, FIG. 14(b) is a top view of the connecting member, FIG. 14(c) is a front view, and FIG. 14(d) is a bottom view. The members common to Embodiment 1 are indicated by the same numbers. 50 is a connecting member, 51a is an upper threaded portion, 51b is a lower threaded portion, 51c is an upper parallel portion, 51d is a lower parallel portion, and 51e is an intermediate portion. 51f is the lower end surface of the lower parallel portion 51d, and 51g is the upper end surface of the upper parallel portion 51c. The upper parallel portion 51(c) and the lower parallel portion 51(d) are used to fasten the connecting member 50 and the audio equipment or the connecting member 50 and the present insulator using a tool such as a spanner. 52 is a speaker, 53 is an upper member, 54 is a screw hole formed in the center of this upper member, 55 is the bottom surface of this screw hole, and 56 is a recess formed in the center of the bottom surface of this screw hole for receiving the spike tip. is. Reference numeral 57 denotes spike screw portions 57 and 58 formed on the bottom surface of the speaker 52, the upper end surface of the upper member 53, and 59 the bottom surface of the speaker. If the outer diameter of the upper threaded portion 51a is φD _a and the outer diameter of the lower threaded portion _51b is φDb, then φD _a <φD _b . This configuration enables the following.

(1) Using the upper parallel portion 51c, the connecting member 50 is fastened to the upper member 53 by rotating it in the direction of the arrow AA in the drawing with a tool such as a spanner. The connecting member 50 descends into the upper member 53 until the lower end surface 51f of the connecting member 50 reaches the bottom surface 55 of the screw hole.
(2) This insulator integrated with the connecting member 50 is rotated in the direction of the arrow BB in the drawing, and the upper threaded portion 51a is fastened to the spike threaded portion 57 of the speaker 52 . In this case, since the outer diameter φD _b of the lower threaded portion > the outer diameter φD _a of the upper threaded portion, the connecting member 50 is restricted from entering the spike threaded portion 57 .
(3) Even when removing the present insulator from the speaker screw portion, the upper parallel portion 51(c) or the lower parallel portion 51(d) can be used to easily remove the connecting member 50 with a tool such as a wrench. be.

First, using the fastening method according to this embodiment, the four insulators are screwed to the speaker. Next, by additionally arranging the insulator of the same specification under the bottom surface of the speaker without screwing, and adjusting the spring rigidity parallel sum K, it is possible to obtain the optimum resonance frequency f ₀ according to the speaker mass m. . The resonant frequency f ₀ in this case is

Fig. 15(a) is a diagram showing four insulators screwed to the speaker, and Fig. 15(b) is a diagram in which two insulators without screws are additionally arranged under the bottom surface of the speaker. In FIG. 15(a), 100 is a speaker, 101a to 101d are insulators fastened to the speaker, and 102a to 102d are connecting members of the insulators. In Fig. 14(b), since the insulators are completely fixed to the four corners of the bottom surface of the speaker, even if the additional insulators are separated from the bottom surface of the speaker due to shock disturbance, the installation stability of the speaker body will be lost. no. The number of insulators to be additionally arranged may be one at the center of the bottom surface of the speaker, or may be three to four. The reason why the spring stiffness of the entire insulator that supports the speaker can be adjusted as a simple parallel sum K (=n×K ₀ ) of the spring stiffness K ₀ of each insulator depends on the structure of the connecting member 50 . In the case of the connecting member 26 in Embodiment 1, when the insulator and the speaker bottom surface are completely fastened, the speaker bottom surface is installed so as to float above the upper member by the thickness of the intermediate portion 27c. In this embodiment, as shown in FIG. 15(b), when the insulator and the speaker bottom surface are completely fastened, the upper end surface 58 of the upper member and the speaker bottom surface 59 are in close contact with each other. As a result, the amount of spring deformation can be made the same between the screw-fastened insulator and the non-screw-fastened insulator, making it easy to set the optimum resonance frequency (Equation (11)).

[Seventh Embodiment]
FIG. 16 is a front cross-sectional view of an audio insulator according to Embodiment 7 of the present invention, in which sound quality was evaluated with the spike attached to the speaker before the insulator of the present invention and the speaker were fastened with a connecting member. A case where this insulator is applied for In FIG. 16, 150 is a speaker and 151 is a spike. By applying the sixth embodiment, this insulator is applied as a floating type spike support structure. The tip of the spike 151 is housed in a recess 56 formed in the center of the bottom surface 55 of the screw hole. Audio speakers are often used with standard spike support. According to the method of this embodiment, (1) the spike is detached from the speaker. (2) Lift the bottom of the speaker. (3) The insulator of the present invention and the speaker are fastened with a connecting member. The above operations (1) to (3) can be omitted at once, and the sound quality improvement effect of the present invention can be easily experienced.

[Eighth embodiment]
In the above-described embodiment, a plurality of retaining members for preventing detachment of the spherical member held between the upper and lower members are provided in the circumferential direction with respect to the axis. In this embodiment, the retaining member is arranged on the central axis of the upper and lower members.

17(a) is a front cross-sectional view of an audio insulator according to Embodiment 8 of the present invention, and FIG. 17(b) is a cross-sectional view along line AA of FIG. 17(a). 701 is an upper member, 702 is a lower member, 703 is a load bearing member, and 704 is an intermediate member. 705a, 705b and 705c are spherical members. 706a, 706b, and 706c are lower recesses for accommodating the spherical members. Reference numeral 707 denotes an upper depression, which is formed in a ring shape on the bottom surface of the upper member 701 . The spherical member interposed between the upper recessed portion and the lower recessed portion does not come off even when the upper member 701 rotates about the axis. 708 is a retaining member, 709 is a through hole formed in the intermediate member and penetrates the retaining member, and 710 is a fastening portion of the retaining member in the upper member. This retaining member can prevent the upper member 701 and the intermediate member 704 from coming off, as in the above-described embodiment. A gap is set so that the outer peripheral portion of the retaining member and the inner peripheral surface of the through hole, and the head portion of the retaining member and the bottom surface of the intermediate member are kept in a non-contact state at all times. A cylindrical sleeve 711 is fixed to the outer periphery of the upper member 701 . In this embodiment, the ring-shaped depression 707 formed on the upper member side may be formed on the intermediate member side.

[Ninth Embodiment]
FIG. 18 is a front cross-sectional view of a ninth embodiment of the present invention, in which a retaining member is provided between the upper member and the lower member to prevent separation of the upper member and the intermediate member. 750 is an upper member, 751 is an intermediate member, 752 is a lower member, 753 is a cylindrical displacement regulating portion formed at the center of the lower member, and 754 is the center formed at the center of the displacement regulating portion. This is the through hole of the shaft. 755 is a fastening bolt that is a retaining member, 756 is a through hole that penetrates the retaining member formed in the intermediate member, 757a, 757b and 757c are spherical members, and 758a, 758b and 758c house the spherical members. It is a lower recessed part to do. Reference numeral 759 denotes an upper depression, which is formed in a ring shape on the bottom surface of the upper member 750 . As in the above-described embodiment, the spherical member interposed between the upper recessed portion and the lower recessed portion does not come off even when the upper member rotates about the axis. The spherical member, the upper hollow portion, and the upper hollow portion can constitute a thrust ball portion having low rigidity in the horizontal direction. By utilizing this point, it is possible to obtain the "slight vibration/seismic isolation slider effect" obtained when the horizontal stiffness is sufficiently smaller than the vertical stiffness of the elastic support member in the range of fine vibration. It is similar to the embodiment described above. 760 is a cylindrical sleeve fixed to the outer periphery of the upper member, 761 is a load support portion, and 762 is a fastening member that is fastened to the side of the mounted equipment. be.

In this embodiment, the fastening bolt 755 is configured to prevent separation of the upper member and the intermediate member. The amount of upward movement of the upper member 750 is restricted by the gap between the lower end surface 764 of the displacement restricting portion 753 and the head portion 765 of the fastening bolt. The structure of this embodiment in which the hooking means is provided between the upper member and the lower member can also be applied to the other embodiments described above.

[Tenth embodiment]
All of the load bearing members applied to the above-described embodiments show the case of applying the damping material in which the spring coil is embedded inside the viscoelastic rubber. In this embodiment, the load supporting member is composed of a single spring coil and a surging prevention member (viscoelastic rubber) arranged in close contact with the metal portion of the spring coil. FIG. 19(a) is a top view of an audio insulator according to Embodiment 10 of the present invention, and FIG. 19(b) is a front cross-sectional view. Not only the vibration damping material described above, but also when the spring coil alone and the upper member are brought into close contact, they are affected by vibration damping. It has been found that the higher the stiffness of the spring coil, for example, the larger the wire diameter of the spring coil under the same outer diameter and height conditions, the greater the vibration damping effect that the upper sleeve receives from the spring coil. The reason for this is that the higher the stiffness of the spring coil, the larger the contact surface area between the upper sleeve and the spring coil. Reference numeral 350 denotes an upper member; 351, a lower member having an L-shaped cross section on one side; 352, a spring coil; 353, a central cylindrical portion of the lower member; , 355 is an intermediate member, and 356 is a spherical member (point contact member), which is composed of three spheres (356a, 356b, 356c). Numerals 357a, 357b, and 357c denote depressions formed on the upper surface of the intermediate member to accommodate the spherical members, and numerals 358a, 358b, and 358c denote depressions formed on the lower surface of the upper member to accommodate the spherical members. 359a, 359b, and 359c are retaining pins, and 360a, 360b, and 360c are through-holes that penetrate the retaining pins formed in the intermediate member (357b, 358b, 359b, and 360b are not shown). 361 is a fixing sleeve, and 362 is a connecting member (the speaker is not shown).

[Eleventh Embodiment]
This embodiment intends to further improve the case where the load supporting member in which the spring coil and the viscoelastic rubber are separated as shown in the tenth embodiment is used. That is, as described in the first embodiment, this shows a measure for avoiding the "contact resonance" of the spherical member supported by point contact with the upper and lower members. FIG. 20 is a front sectional view of an audio insulator according to Embodiment 11 of the present invention, and 380 is a surging prevention member (viscoelastic rubber) arranged in close contact with the spring coil. The insulator structure of this embodiment is the same as that of the tenth embodiment except for the shape of the surge prevention member 380 . Incidentally, the surging prevention member is used as a means for avoiding the surge resonance phenomenon peculiar to spring coils. In this embodiment, by setting the axial lengths of the spring coil 352 and the surging prevention member 380 to the same dimension or the same level of dimension, the upper end surface 381 of the surging prevention member 380 and the lower end surface 382 of the intermediate member 355 are arranged. The close contact avoids the "contact resonance" of the spherical member. In this embodiment, the upper end surface 381 of the surging prevention member 380 is arranged substantially directly below the spherical member 356 . Further, the resonance phenomenon of the intermediate member 355 alone can be avoided due to the vibration damping action of the surge prevention member 380 . Therefore, the intermediate member can be manufactured with a thin plate structure that can be press-worked, and the cost can be greatly reduced.

[Twelfth embodiment]
FIG. 21 shows a twelfth embodiment of the present invention, in which springs are used to adjust the upper and lower limits in order to improve the installation stability of the device to be protected (for example, a speaker) mounted on the insulator. It is provided using the internal space of the That is, as will be described later, a floating type "pseudo-rigidizing unit" is configured.

21(a) is a top view, and FIG. 21(b) is a cross-sectional view taken along line AA of FIG. 21(a). 450 is an upper member, 451 is a lower member, 452 is a spring coil, 453 is an intermediate member, 454a and 454b are positioning portions for the spring coils, and 455 is a projection on the upper surface of the upper member. A connection member 456 is fixed to the upper surface convex portion 455 and fastened to a device 457 (indicated by an imaginary line) to be protected. A central shaft 458 is fastened to the upper member and protrudes toward the lower member, and 459a and 459b are a lower limit adjusting nut and an upper limit adjusting nut fastened to the central shaft. Reference numeral 460 denotes a cylindrical displacement restricting portion formed at the center of the lower member, and 461 denotes a through hole for the central shaft formed at the center of the displacement restricting portion. The upward movement amount (upper limit clearance) δV ₂ of the upper member 450 is set by the clearance between the lower end surface 462 of the displacement restricting portion 460 and the upper limit adjustment nut 459b. A downward movement amount (lower limit gap) δV ₁ of the upper member 450 is set by the gap between the upper end surface 463 of the displacement restricting portion 460 and the lower limit adjusting nut 459a. A gap between the outer peripheral surface of the central shaft 458 and the facing surface of the displacement restricting portion 460 restricts the amount of horizontal movement δH (δH is not shown). That is, by effectively utilizing the internal space of the spring coil 452, the locations where δV ₁ , δV ₂ , and δH are set are provided close to each other.

464 is a surge resonance prevention member, and 465 is a spherical member (point contact member), which is composed of three spheres (465a, 465b, 465c). 466a, 466b and 466c are recessed portions formed on the lower surface of the upper member to accommodate the spherical members, and 467a, 467b and 467c are recessed portions to accommodate the spherical members formed on the upper surface of the intermediate member. 468a, 468b, and 468c are retaining pins, and 469a, 469b, and 469c are through holes (466b, 467b, and 469b are not shown) that penetrate the retaining pins formed in the intermediate member. 470 is a fixing sleeve, and 471a, 471b, and 471b are bolts for fastening the connecting member 456 to the upper surface protrusion 455 of the upper member. 472 is a floor surface, 473 is a board provided between the insulator and the floor surface 472, and 474a and 474b are bolts (other bolts are not shown) for fastening the board 473 and the lower member 451 together. A through hole 475 is formed in the intermediate member 453 . The central shaft passes through the through hole 475 without contact and is fastened to the fastening portion 476 of the upper member. If the device 457 to be protected is, for example, a speaker, the connection member 356 is fastened to the spike screw portion using the spike screw portion on the bottom surface of the speaker.

Here, (1) elastic support members (spring coils) that support the load of the equipment to be protected, (2) means for restricting the amount of movement of the elastic support members with narrow gaps (δV ₁ , δV ₂ , δH), the above ( A vibration isolation structure that incorporates 1) and (2) in a single unit is called a floating-type “pseudo-rigid unit”. Even in an emergency when a large external force is applied to the equipment to be protected, the device to be protected can be prevented from overturning by means of restricting the narrow gap of the "pseudo-rigid unit". Further, since the central shaft penetrates through the through hole 475 of the intermediate member without contact, external impact force that damages the spherical member and the recessed portion is not applied.

[Thirteenth embodiment]
FIG. 22 shows an audio insulator according to a thirteenth embodiment of the present invention, in which an upper sleeve called a wind chime member is arranged instead of the upper member applied to the insulator of the first embodiment. An audio insulator that improves acoustic characteristics by utilizing the high-frequency vibration assist effect of a wind chime member has already been proposed by the inventors of the present invention, and is already known from Patent Documents 1 and 2.

22(a) is a top view, and FIG. 22(b) is a cross-sectional view taken along line AA of FIG. 22(a). The members common to Embodiment 1 are indicated by the same numbers. Reference numeral 801 denotes an upper sleeve (an upper member which is a resonance member), 802 a lower member, 803 a device mounting portion on which the audio device 25 is mounted on the upper end surface of the upper sleeve, and 804 an insulator installation surface (floor surface). In this embodiment, the upper sleeve 801 is made of brass, which has good properties as an acoustic material. The upper sleeve is configured for the purpose of adjusting (improving) the acoustic characteristics of the audio equipment in the high frequency range. That is, the inside of the upper sleeve has a cavity that accommodates the load support portion 13, the intermediate member 15, and the spherical member 16, one end of which has a closed structure, and the other end of which is open to the atmosphere (free end). It has a cylindrical shape, that is, a shape close to a "wind chime". The upper end of the upper sleeve 801 is not completely fixed so that the wind chime can be hung by a string and play a strange tone. The member is interposed and elastically supported by the load supporting portion.

The voice coil reaction force of the speaker placed on the upper surface of the upper sleeve 801 excites the insulator. Various high-frequency vibration modes are excited by the excitation force F in the upper sleeve 801 supported by the load support portion 13 through the spherical member and the intermediate member. In addition to these resonance modes, the acoustic vibration characteristics of the wind chimes (upper sleeve 801), which have reverberations and fluctuations, bring about sound image localization, resolution, transparency, scale, and other acoustic characteristics improvement effects (wind chime effects). be.

In the proposed insulator (Patent Document 2) shown in FIG. 30, since the vibration transmission path of "the tapered portion 519 of the upper sleeve 511→the spherical member 516" is a point contact, the upper sleeve receives vibration from the spring coil. It is said that the damping effect is greatly reduced. However, in the above structure, a radial component force directed toward the center acts on the upper portion of the spherical member due to the axial load applied to the contact surface with the tapered portion 519 . In addition, the lower portion of the spherical member is housed in a recessed portion 518 to restrict its movement in the radial direction. Therefore, at equilibrium, the horizontal stiffness of the upper sleeve with respect to the intermediate plate 515 is K _x =∞.

In this embodiment shown in FIG. 22, the horizontal stiffness _Kx of the upper sleeve with respect to the intermediate member 15 can be made sufficiently small, as explained in detail in the first embodiment. That is, since the spherical member supports the upper sleeve in point contact and in a rollable manner, the restraint conditions that the upper sleeve receives are further reduced. As a result, the acoustic characteristics can be further improved by the wind chime effect.

[14th embodiment]
FIG. 23 shows a fourteenth embodiment of the present invention, in which viscoelastic rubber is used in place of the spring coil for the load supporting portion. With this configuration, a simpler and thinner vibration isolation unit can be realized. 23(a) is a view taken along line BB of FIG. 23(b), and FIG. 23(b) is a cross-sectional view along line AA of FIG. 23(a). 821 is an upper member, 822 is a lower member, 823 is an intermediate member, and 824 is a load bearing member made of cylindrical viscoelastic rubber that supports the load of the mounted equipment. 825 is a sleeve, 826 is a thrust washer, 827 is a bolt, and 828 is mounted equipment.

23(a) and 23(b), 829a is a protrusion on the bottom surface of the intermediate member 823, 829b is a recess on the bottom surface of the intermediate member, and 830 is the upper end surface of the viscoelastic rubber. The bottom surface of the intermediate member has the protrusions and the recesses alternately formed in the circumferential direction, and the protrusions are in close contact with the upper end surface 830 of the viscoelastic rubber. The angle at which the projection is formed is θ ₂ , and the angle at which the projection and the recess are formed is θ ₁ +θ ₂ . At this time, the angle at which the bottom surface 830 of the intermediate member contacts the upper end surface of the viscoelastic rubber is reduced to Φ=θ ₂ /(θ ₁ +θ ₂ ) in this embodiment. The value of Φ controls the magnitude of the damping effect. A spherical member (point contact member) 831 is composed of three spheres (831a, 831b, 831c). 832a, 832b and 832c are upper depressions formed on the lower surface of the upper member to accommodate the spherical members, and 833a, 833b and 833c are lower depressions to accommodate the spherical members formed on the upper surface of the intermediate member. (832a, 832c, 833a, 833c not shown).

[15th embodiment]
FIG. 24 shows a fifteenth embodiment of the present invention, which makes further use of the feature that the thrust ball portion can have low rigidity in the horizontal direction. That is, the spherical members are housed in the recesses formed in the two opposing surfaces, respectively, to form a set of thrust ball portions. Further, by stacking the thrust ball portions in multiple stages, a multi-stage thrust ball unit is constructed. As a result, attention was paid to the fact that it is possible to further reduce the rigidity in the horizontal direction and increase the stroke. This embodiment has a two-stage unit configuration.

24(a) is a top view of the multi-stage thrust ball unit, FIG. 24(b) is a sectional view along AA in FIG. 24(a), and FIG. 24(c) is a sectional view along BB in FIG. 24(a). 601 is the first member, 602 is the second member, 603 is the third member, 604a, 604b and 604c are spherical members sandwiched between the first member and the second member, A spherical member sandwiched between the second member and the third member. 606a, 606b, and 606c are retaining members, 607 is a connecting member, and 608 is a load supporting portion. That is, the intermediate member is composed of a first member 601, a second member 602, and a third member 603, which are plate-like members. Reference numerals 609a, 609b, and 609c denote through holes formed in the first member 601 that pass through the retainer member, and 610a, 610b, and 610c denote through holes formed in the second member 602 that pass through the retainer member. The retaining member is fastened to the third member 603 by screw portions 611a, 611b, and 611c. A radial clearance δr between the retainer member and the through hole is set within the permissible range of the radial stroke of the multi-stage thrust ball unit. A vertical gap δz between the retaining member and the first member 601 is set within a range in which the spherical member cannot be separated.

The two-stage thrust ball unit of this embodiment can reduce the horizontal stiffness to 1/2 and increase the horizontal stroke by a factor of 2 compared to a single set of thrust ball sections.

An elastic support member such as a spring coil, an air spring, a spring utilizing the repulsive force of a magnet, or viscoelastic rubber can be applied to the load support portion 608 according to the application. Alternatively, it may be installed on a rigid body that does not deform elastically.

[16th embodiment]
FIG. 25 shows a seventeenth embodiment of the present invention, in which a multi-stage thrust ball unit is provided with horizontal damping action. FIG. 25 is a front cross-sectional view of the three-stage thrust ball unit of this embodiment, which corresponds to the AA cross-sectional view of FIG. 24(a). A drawing showing a retaining member corresponding to FIG. 24(c) is not shown. 651 is the first member, 652 is the second member, 653 is the third member, and 654 is the fourth member. 655a, 655b, 655c are spherical members sandwiched between the first member and the second member; 656a, 656b, 656c are spherical members sandwiched between the second member and the third member; 657b and 657c are spherical members sandwiched between the third member and the fourth member. (655c, 656c, 657c) are not shown.

Here, the intermediate member is a plurality of plate-like members, which correspond to a first member 651, a second member 652, and a third member 653, which are separated from each other by a predetermined distance in the axial direction. In this embodiment, the intermediate member is housed within a fourth member 654 which is a cylindrical fixed member with one end open. The inner side surface of the fourth member 654 and the outer side surfaces of the first member 651, the second member 652, and the third member 653 are arranged to face each other.

658 is a connecting member, 659 is a device to be protected (indicated by a two-dot chain line), 660 is a load support, and 661 is a floor surface. A low-rigidity O-ring 662 is sandwiched between the first member and the fourth member, and provides gentle damping action in the horizontal direction of the first member. The O-ring 662 also serves as a dust-proof seal for preventing dust from entering the space in which the spherical member is accommodated. The measure of providing a damping action and a dust-proof seal between the fixed member (corresponding to the fourth member) and the movable member (corresponding to the first member) is also effective for each of the above-described embodiments.

[17th embodiment]
FIG. 26 shows Embodiment 17 of the present invention. All of the above-described embodiments show configurations in which the thrust ball portion is arranged on the mounted device side (under the upper member), and the load support portion, which is the elastic support member, is arranged below the thrust ball portion. The locations of the thrust ball portion and the load bearing portion may be reversed if the application takes advantage of the feature of the previously described embodiment in which the low stiffness characteristic of the thrust ball portion can be selected independently of the stiffness of the resilient support member.

That is, in this embodiment the intermediate member is positioned between the upper member and the floor rather than between the upper member and the load bearing portion. Also, the audio equipment is not directly placed on the upper surface of the upper member, but is arranged on the upper surface side of the upper member via the load support portion.

Hereinafter, members common to those of the fifteenth embodiment are denoted by the same numbers. Reference numeral 951 denotes a load support portion which is an elastic support member; 952, mounted equipment; 953, a connection member for connecting the load support portion side and the mounted equipment; and 954, a floor surface. The configuration in which the positions of the thrust ball portion and the load bearing portion are reversed can be applied to any of the above-described embodiments, and does not affect the vertical and horizontal stiffness of the entire unit.

[18th Embodiment]
FIG. 27 shows an eighteenth embodiment of the present invention, which is stable against buckling by combining a thrust ball portion with low rigidity in the horizontal direction and a plurality of small-diameter spring coils. , and has even lower rigidity characteristics in the horizontal direction. FIG. 27(a) is a top view, and FIG. 27(b) is a sectional view taken along the line AA of FIG. 27(a). Reference numeral 400 denotes an upper member; 401, a lower member; and 402a, 402b, and 402c, spring coils which are equally divided into three portions in the circumferential direction. Reference numerals 403a, 403b, and 403c denote base portions, and 404a, 404b, and 404c denote surging prevention members adhered to the upper portions of the base portions and attached to the inner surfaces of the spring coils. The spring coil and the surge prevention member constitute a load support member.

An intermediate member 405 and a spherical member (point contact member) 406 are composed of three spheres (406a, 406b, 406c). 407a, 407b and 407c are recesses formed on the upper surface of the intermediate member to accommodate the spherical members, and 408a, 408b and 408c are recesses formed on the lower surface of the upper member to accommodate the spherical members. 409a, 409b, and 409c are retaining pins, and 410a, 410b, and 410c are through holes (407c, 408c, and 410c are not shown) that penetrate the retaining pins formed in the intermediate member. 411 is a connecting member that connects the present insulator and mounted equipment.

Now, the vertical spring constant _KV of the spring coil that constitutes the load supporting member of this embodiment is obtained by the following equation. If N is the effective number of turns of the spring coil, D is the average diameter of the coil, d is the wire diameter of the coil, and G is the transverse elastic modulus, then the vertical spring constant K _V is

Assuming that the horizontal spring constant is K _H and the shear modulus of the material is G=11.510 psi (≒8000 kg/mm), the ratio of K _V to K _H is given by Grede's formula:

As shown in FIG. 26, D is the average diameter of the spring coil and _hs is the height in use.
From equation (13), K _H <<K _V can be established by sufficiently reducing D. 27, in which a plurality of spring coils having a sufficiently small average diameter D are arranged in the circumferential direction, a spring unit that is stable against buckling and has low rigidity in the horizontal direction can be constructed. However, since the spring coil diameter D also affects the vertical stiffness according to formula (12), there is a limit to the range of choices for vertical and horizontal stiffness in response to the requirements of the application.

In this embodiment, by combining the spring unit and the thrust ball, it is possible to select the optimum horizontal stiffness required by the application without affecting the vertical stiffness of the spring unit.

[Nineteenth Embodiment]
FIG. 28 shows an audio insulator according to Embodiment 19 of the present invention, in which each unit is composed of one thrust ball. FIG. 28(a) is a top view, and FIG. 28(b) is a sectional view taken along the line AA of FIG. 28(a). On-board equipment 902 is supported by three units 901a, 901b, 901c. Attention will be paid to the unit 901a. The members common to Embodiment 1 are indicated by the same numbers. 903 is an upper member, 904 is an intermediate member, 905 is a spherical member, 906(a) and 906(b) are retaining members, and 907 is a connecting member. The spherical member is held by recesses (not numbered) formed in the upper member and the lower member. Since each unit in this embodiment has one spherical member, the installation of the unit as a single unit is unstable. However, as shown in FIG. 28(a), if a plurality of sensors are installed on the on-board equipment, the installation conditions for the entire system are stabilized. In addition, as shown in this embodiment, if the system is installed at three locations, redundancy (inconsistency) of the supporting portions is completely eliminated in the system as a whole, so installation resonance can be completely avoided.

[supplement]
(1) Condition of Resonance Frequency of Thrust Ball Portion Supplementary explanation is given regarding the case of applying a thrust ball portion in which the upper member and the intermediate member are configured to be relatively movable in the horizontal direction. The floor surface of a private house where speakers are installed usually has a distributed vibration mode with an eigenvalue of 20 to 100Hz. As described above, when the vibration of the speaker is transmitted to the floor, it excites the complex natural vibration modes of the entire room including the floor. In order to avoid the deterioration of sound quality caused by mutual interference between low-frequency floor vibration and speaker vibration, we set the upper limit of the natural frequency of the floating insulator to a value that is not affected by floor vibration. There is a need to. FIG. 29 shows the vibration isolation performance versus frequency obtained when the natural frequency is f ₀ =8 Hz and f ₀ =15 Hz. The vibration isolation characteristic has a characteristic (base) that slopes with respect to frequency, centering on the resonance point _f0 . In order to avoid the influence of floor vibration, it is a necessary condition that the vibration isolation performance < 0 in the area where the floor has a distributed vibration mode. The allowable upper limit of the natural frequency including point B in the figure is f ₀ =f _B =15 Hz.

For example, in the case of the insulator of the first embodiment, the horizontal spring stiffness K _HSUM of the insulator main body is determined by the parallel sum of the spring stiffness K _X0 of the thrust ball portion 16 and the spring stiffness K _H of the load support portion 13 . That is, K _HSUM =K _X0 ×K _H /(K _X0 +K _H ). The horizontal resonance frequency f _0SUM of the insulator main body is determined by the parallel sum K _HSUM of the mass M of the payload and the spring stiffness, and is f _0SUM =(1/2π)×(M/K _HSUM ) ⁻¹ . Therefore, if the resonance frequency of the thrust ball portion is set to f _X0 <15 Hz, it is possible to maintain the necessary condition of f _0SUM <15 Hz for avoiding the influence of floor vibration, regardless of the value of the resonance frequency of the load support portion alone. Furthermore, by setting the resonance frequency of the thrust ball portion to f _X0 <8 Hz, it is possible to realize an insulator having a low horizontal resonance frequency, which has been practically difficult in terms of installation stability. The reason for this is that when the resonance frequency f _H without the thrust ball portion is compared with the resonance frequency f _X0 of the thrust ball portion that does not depend on the mass of the mounted object, f _X0 <<f _H can be obtained. This is because the resonance frequency _f0SUM is governed by the above _fX0 . Also, (1) the horizontal movement of the thrust ball is constrained, on the order of 0.5 to 1.0 mm centered on the equilibrium point. (2) The vertical stiffness of the thrust ball is K _{XZ ≈∞} . For the reasons (1) and (2) above, the presence of the thrust ball does not affect the installation stability of the device. However, when the load is supported by the spring coil alone, both f _H and f _V have to be 8 to 15 Hz due to the required installation stability and vibration isolation performance.

(2) Spherical member The depressions (for example, 17 and 18 in Fig. 1) for housing the spherical member need not be perfectly circular. The horizontal resonance frequency f _SX0 of the thrust ball portion at the equilibrium point does not depend on the mass M of the payload, and is the radius R ₁ of the spherical member 16a, the curvature radius R _2A of the upper recess 18a, and the curvature radius R of the lower recess 17a. Determined by _2B alone. for that reason,
(i) In the vicinity of the equilibrium point θ≈0, the radii of curvature R _2A and R _2B are sufficiently large. (ii) At a point away from the equilibrium point, the radii of curvature R _2A and R _2B are formed small.

A non-perfect circular shape formed by a combination of (i) and (ii) above may also be used. With the above configuration, the resonance frequency f _SX0 at the equilibrium point can be set sufficiently low, and the settling time required for alignment to the equilibrium point can be shortened when a large external force is applied to the upper member.

The spherical member (16 in FIG. 1, for example) and the recesses (17 and 18 in FIG. 1) can be made of various materials with different specific acoustic impedances, such as brass, steel, ceramics, quartz, and resin. The spherical member (point contact member) is composed of three spheres, and this number of three is the minimum required and optimum number of support shafts when handling the insulator alone. The reason for this is that if there are two or fewer, stable support is not possible, and if there are four or more, the support conditions become unstable, and the presence of non-contact support (play) in the vibration transmission path may cause distortion. for it arises.

(3) Structure of "Hanging" In the structure of "Hanging" in the thrust ball portion, contrary to the first embodiment, the retaining member is fixed to the intermediate member side, and the retaining member is normally attached to the above-mentioned It may be configured to maintain a non-contact state with respect to the upper member. 30, 950 is an upper member, 951 is an intermediate member, 952 is a spherical member, 953 is an upper depression, 954 is a lower depression, and 955 is a load bearing portion. 956 is the retaining member, 957 is the head of the retaining member, 958 is the intermediate portion, 959 is the screw fastening portion between the intermediate member 951 and the retaining member, and 960 is the retaining member formed on the upper member side. This is the storage part for the head. The interval (play gap range) in which the upper member and the intermediate member can move relative to each other is determined by the position of the head of the retaining member and the position of the bottom surface of the storage portion, and is .delta.n. When the maximum depth of the upper depression is δa and the maximum depth of the lower depression is δb,

If the above formula is satisfied, the spherical member will not be separated from the thrust ball portion. The condition of formula (14) is the same for other examples including the first embodiment.

(4) Upper Member When the present invention is applied to audio equipment, the upper member can be selected from various materials such as brass, steel, ceramics, wood, and resin. If a high-quality acoustic material such as brass is used for the upper member, the acoustic characteristics will be greatly affected even if the resonance frequency exceeds the audible range (10,000 Hz or higher).

For example, noting that the intermediate member 15 in Embodiment 1 can be a pressed thin plate component, a structure in which a thin plate component having substantially the same shape is fixed to the bottom surface side of the upper member may be employed. This thin plate part is formed with a recess, a through hole for a retaining pin, and the like. That is, the configuration is such that the spherical member 16 is sandwiched between the upper and lower thin plate parts. With the above configuration, the upper member can be simplified to a structure that does not require curved surface processing of the recessed portion, so that the upper member can be selected from many materials, and the cost can be greatly reduced.

The horizontal resonance frequency _fX0 of the thrust ball portion may be selected from among balls having different outer diameters while sharing a pair of upper and lower recesses having the same radius of curvature. In the case of steel balls used in ball bearings and the like, spheres with slightly different outer diameters are standardized in many stages and easily available. Using this point, the optimum horizontal resonance frequency _fX0 can be selected with high accuracy.

In the above-described embodiments, the case where the insulator of the present invention is applied to a speaker has been shown, but it can be applied to audio equipment such as CD players, analog players, preamplifiers, power amplifiers, various musical instruments (for example, acoustic instruments), pianos, and the like. Either can be applied and the same effect can be obtained. Further, in the embodiment, all the insulators are arranged vertically on the floor surface, but the insulators can be horizontally arranged, for example, when the audio equipment is horizontally arranged on the wall surface.

In the above-described embodiments, the elastic support member (load support portion) combined with the point contact member is a vibration damping part or a spring coil. The elastic supporting member applicable to the present invention is not limited to this. Shapes required for audio insulators include, for example, conical coil springs, disk springs, structures in which these disk springs are stacked in multiple stages, bamboo springs, ring springs, spiral springs, thin leaf springs, laminated leaf springs, and U-shaped springs. , dimensions, etc., should be considered. In addition to the spring coil, a floating type insulator such as one using the repulsive force of a magnet, one using a wire and a U-shaped spring, and an air type can also be applied. Specifically, for example, the lower unit 13 in FIG. 2B may be replaced with a member constituting the floating system described above.

It is assumed that the present invention is applied to, for example, a vibration isolator supported by air springs. 2. Description of the Related Art Semiconductor manufacturing equipment such as exposure equipment, electron microscopes, and precision instruments such as three-dimensional measuring instruments are used in a state in which microvibrations from the installation floor are insulated. To improve the performance of an air spring supported vibration isolator, it is necessary to lower its natural frequency. The natural frequency of the air spring in the vertical direction can be lowered by enlarging the air chamber of the air spring, but the natural frequency in the horizontal direction cannot be lowered by the same means. Therefore, in order to reduce the horizontal natural frequency of the vibration isolator, a laminated rubber having low horizontal rigidity is arranged above or below the air spring. However, laminated rubber has the drawback that its natural frequency changes when the applied load changes, and the supporting area of the placed object becomes unstable due to the decrease in the support area due to shear deformation. have. By applying the thrust ball unit of the present invention in combination with an air spring or a spring coil, even though the natural frequency in the horizontal direction is small, even if the applied load changes, the natural frequency changes. It is possible to realize an anti-vibration device with less vibration and stable support of the placed object. For example, in the case of an electron microscope, positioning accuracy in the horizontal direction is important, and it is effective for a vibration isolator combining a thrust ball and a load supporting means, which can obtain excellent vibration isolation performance in the horizontal direction.

By covering the entire unit of the present invention with a stretchable dust-proof film (for example, a bellows-shaped surrounding portion), a sealed structure is provided. This sealed structure can protect the thrust ball, which is composed of the spherical member and the recessed portion, from the influence of dust. In addition, it is possible to permanently prevent deterioration of the compression coil spring, surge prevention member, and the like due to wind, rain, and ultraviolet rays.

Reference Signs List 11 Upper member 25 Audio device 13 Load supporting portion 15 Intermediate member 16 Point contact member 19 Retaining means 12 Lower member

Claims (22)

an upper member having an audio device arranged on the upper surface side;
a load support section made of an elastic member that supports the load of the audio device;
an intermediate member interposed between the load bearing portion and the upper member, or interposed between the upper member and a floor surface;
A point contact member interposed between the upper member and the intermediate member and in point contact with the upper member or the intermediate member;
hooking means for hooking the distance between the intermediate member and the upper member so as to be variable within a predetermined value;
an end surface of the intermediate member on the side of the load supporting portion is in close contact with a viscoelastic material;
The load-bearing part is
a viscoelastic rubber, which is a viscoelastic material;
and a spring coil embedded in the viscoelastic rubber. 2. An audio according to claim 1, wherein said hooking means has one end fixed to either said intermediate member or said upper member and the other end configured to hook to either said upper member or said intermediate member. insulator. the load bearing portion is disposed between the upper member and a floor;
2. The audio insulator according to claim 1, wherein said intermediate member is pressed toward said upper member by said load support portion. A plurality of said hooking means are provided between said upper member and said intermediate member,
3. The audio insulator according to claim 1, wherein said hooking means is provided at a location away from the axis of said upper member and substantially concentrically with respect to said axis. 5. The audio insulator according to claim 4, wherein a threaded portion for a connecting member that connects the bottom surface of the audio equipment and the upper member is formed in the central portion of the upper member. an upper member having an audio device arranged on the upper surface side;
a load support section made of an elastic member that supports the load of the audio device;
an intermediate member interposed between the load bearing portion and the upper member, or interposed between the upper member and a floor surface;
A point contact member interposed between the upper member and the intermediate member and in point contact with the upper member or the intermediate member;
hooking means for hooking the distance between the intermediate member and the upper member so as to be variable within a predetermined value;
an end surface of the intermediate member on the side of the load supporting portion is in close contact with a viscoelastic material;
The viscoelastic material is formed in a substantially cylindrical shape,
The audio insulator, wherein the point contact member is arranged at a position radially close to an upper end surface of the viscoelastic material on an end surface of the intermediate member on the upper member side. r _x the distance between the center of the point contact member and the outer surface of the viscoelastic material,
As the distance r ₀ between the outer peripheral edge of the disc-shaped intermediate member and the outer surface of the viscoelastic material,
2. The audio insulator according to claim 1, wherein _rx < _r0 /2. 7. An audio insulator according to claim 6, wherein said intermediate member has an average thickness _hb <3 mm. an upper member having an audio device arranged on the upper surface side;
a load support section made of an elastic member that supports the load of the audio device;
an intermediate member interposed between the load bearing portion and the upper member, or interposed between the upper member and a floor surface;
A point contact member interposed between the upper member and the intermediate member and in point contact with the upper member or the intermediate member;
hooking means for hooking the distance between the intermediate member and the upper member so as to be variable within a predetermined value;
an end surface of the intermediate member on the side of the load supporting portion is in close contact with a viscoelastic material;
The surface on the intermediate member side, which is the surface facing the upper end surface of the viscoelastic material, has a stepped shape in the circumferential direction or the radial direction, and the upper end surface of the viscoelastic material and the surface on the intermediate member side. is partially in close contact with the audio insulator. an upper member having an audio device arranged on the upper surface side;
a load support section made of an elastic member that supports the load of the audio device;
an intermediate member interposed between the load bearing portion and the upper member, or interposed between the upper member and a floor surface;
A point contact member interposed between the upper member and the intermediate member and in point contact with the upper member or the intermediate member;
hooking means for hooking the distance between the intermediate member and the upper member so as to be variable within a predetermined value;
an end surface of the intermediate member on the side of the load supporting portion is in close contact with a viscoelastic material;
The load-bearing part is
spring coil and
and a surge prevention member made of a viscoelastic material for avoiding the surge phenomenon of the spring coil,
An audio insulator, wherein upper end surfaces of the spring coil and the surge prevention member are configured to be in close contact with a surface of the intermediate member. 2. The audio insulator according to claim 1, wherein said point contact member is a spherical member and makes point contact with said upper member and said intermediate member. an upper member having an audio device arranged on the upper surface side;
a load support section made of an elastic member that supports the load of the audio device;
an intermediate member interposed between the load bearing portion and the upper member, or interposed between the upper member and a floor surface;
A point contact member interposed between the upper member and the intermediate member and in point contact with the upper member or the intermediate member;
hooking means for hooking the distance between the intermediate member and the upper member so as to be variable within a predetermined value;
The point contact member is a spherical member and makes point contact with the upper member and the intermediate member;
An upper hollow portion having a curved surface that accommodates a part of the spherical member formed on the surface of the upper member on the intermediate member side, and one part of the spherical member formed on the surface of the intermediate member on the upper member side. a lower recessed portion having a curved surface that houses the portion;
The spherical member is rotatably inserted between the upper recessed portion and the lower recessed portion, and in a balanced state in which the audio device is mounted on the upper surface of the upper member, the upper member and the intermediate member are opposed to each other. 1. An insulator for audio, characterized in that it is substantially horizontally movable. 13. The audio insulator according to claim 12 , wherein said audio device mounted on said upper member is a speaker having a horizontal excitation force. The horizontal resonance frequency of the thrust ball portion composed of the point contact member, the upper member, and the lower member provided below the upper member is f _X0 ,
Let f _H be the resonance frequency determined by the mass of the audio equipment mounted on the upper member and the horizontal rigidity of the load support unit alone,
13. The audio insulator according to claim 12 , wherein _fX0 < _fH . R _2B is the radius of curvature of the upper recess, R _2A is the radius of curvature of the lower recess, R ₁ is the radius of the spherical member, g is the acceleration of gravity, and the horizontal resonance frequency is

, where M is the mass of the audio equipment mounted on the upper member, and K is the horizontal spring _stiffness of the load support unit alone.

year,
15. The audio insulator according to claim 14 , wherein _fX0 < _fH . 15. The audio insulator according to claim 14 , wherein _fX0 <15 Hz. 17. The audio insulator according to claim 16 , wherein _fX0 <8Hz. an upper member having an audio device arranged on the upper surface side;
a load support section made of an elastic member that supports the load of the audio device;
an intermediate member interposed between the load bearing portion and the upper member, or interposed between the upper member and a floor surface;
A point contact member interposed between the upper member and the intermediate member and in point contact with the upper member or the intermediate member;
hooking means for hooking the distance between the intermediate member and the upper member so as to be variable within a predetermined value;
The intermediate member is composed of a plurality of plate-like members spaced apart in the thickness direction,
A spherical member as the point contact member is provided between the upper member and the uppermost plate-like member and between each plate-like member to form a multistage thrust ball portion. audio insulator. The thrust ball portion further comprises a cylindrical fixing member with one end open fixed to the load support portion,
the upper member and the intermediate member are accommodated in the fixing member such that side surfaces of the upper member and the intermediate member face an inner side surface of the fixing member;
3. A sealing means for preventing dust from entering said spherical member constituting said thrust ball portion is provided between a side surface of said upper member and an inner side surface of said fixed member. 19. The audio insulator according to 18 . 20. The audio insulator according to claim 19 , wherein said sealing means also serves as vibration damping means. an upper member having an audio device arranged on the upper surface side;
a load support section made of an elastic member that supports the load of the audio device;
an intermediate member interposed between the load bearing portion and the upper member, or interposed between the upper member and a floor surface;
A point contact member interposed between the upper member and the intermediate member and in point contact with the upper member or the intermediate member;
hooking means for hooking the distance between the intermediate member and the upper member so as to be variable within a predetermined value;
a shaft fixed to the upper member, penetrating the intermediate member in a non-contact manner and extending toward the load supporting portion;
an upper limit regulating portion for regulating the amount of upward movement of the upper member provided between the shaft and a lower member provided below the load supporting portion; and a lower portion of the shaft and the load supporting portion. An audio insulator characterized by comprising a lower limit regulating portion for regulating the amount of downward movement of the upper member provided between the lower members provided on the side. An upper member on which an audio device is arranged on the upper surface side, a load support portion configured by an elastic member for supporting the load of the audio device, and interposed between the load support portion and the upper member, or the upper portion an intermediate member interposed between a member and a floor surface; a spherical member interposed between the upper member and the intermediate member and in point contact with the upper member or the intermediate member; and the intermediate member hooking means for connecting the upper member so that the distance between the upper member can be varied within a predetermined value to prevent the spherical member from being detached from between the intermediate member and the upper member; An upper hollow portion having a curved surface that accommodates a portion of the spherical member formed on the member-side surface, and a curved surface that accommodates a portion of the spherical member formed on the upper member-side surface of the intermediate member. and a lower recessed portion having a lower recessed portion, the upper member and the intermediate member being rotatably inserted between the upper recessed portion and the lower recessed portion, and in a balanced state in which the audio device is mounted on the upper surface of the upper member. is relatively horizontally movable, and a design method for an audio insulator comprising:
a vertical resonance frequency setting step of setting a vertical resonance frequency required for the audio device based on the mass of the audio device and the rigidity of the load support portion;
After the vertical resonance frequency setting step, a horizontal resonance frequency setting step of setting a horizontal resonance frequency from the curvature radii of the upper recess and the lower recess and the radius of the spherical member. A design method for an audio insulator characterized by:

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